US20100093479A1 - Continuously variable transmissions and methods therefor - Google Patents
Continuously variable transmissions and methods therefor Download PDFInfo
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- US20100093479A1 US20100093479A1 US12/526,770 US52677008A US2010093479A1 US 20100093479 A1 US20100093479 A1 US 20100093479A1 US 52677008 A US52677008 A US 52677008A US 2010093479 A1 US2010093479 A1 US 2010093479A1
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- cam
- traction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
- F16H15/26—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution
- F16H15/28—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution with external friction surface
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
- F16H15/50—Gearings providing a continuous range of gear ratios
- F16H15/503—Gearings providing a continuous range of gear ratios in which two members co-operate by means of balls or rollers of uniform effective diameter, not mounted on shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
- F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
- F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
- F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges
Definitions
- the disclosed invention relates generally to mechanical power modulation and transmission. More specifically, the invention concerns continuously variable units and transmissions, subassemblies, components, and methods for use therewith.
- CVT continuously variable transmissions
- the particular type of CVT which pertains to the present disclosure is typically known as a ball-type rolling traction CVT.
- ball-type rolling traction CVTs have gained some acceptance in certain industrial applications, the technology has generally been unable to overcome technical and economic hurdles to gain a wider adoption across multiple fields of use.
- inventive embodiments disclosed here address many of the challenges that have prevented ball-type rolling traction CVTs from gaining wider acceptance in the marketplace.
- inventive embodiments disclosed here provide mechanisms and methods for employing ball-type continuously variable units and/or continuously variable transmissions in automotive applications.
- One aspect of the invention relates to a drive having a prime mover and a transmission coupled to the prime mover.
- the transmission has a continuously variable unit (CVU), an input interface coupled to the prime mover and to the CVU, and an output interface coupled to the CVU.
- the drive also has a parallel branch for mechanical power transmission. The parallel branch can be coupled to the input interface and to the output interface.
- the transmission has a number of traction planets in contact with the input traction ring, and the transmission has a traction sun in contact with the traction planets.
- the transmission has an output traction ring in contact with the traction planets, an output load cam, and a second number of load cam rollers positioned between the output traction ring and the output load cam.
- the transmission has a planetary gearset that has a sun gear, a ring gear, and a carrier. The output load cam is coupled to the ring gear, and the main shaft is coupled to the sun gear.
- the transmission can also have a transfer shaft coupled to the planetary gear set carrier.
- One more aspect of the invention concerns a transmission including a number of traction rollers, a carrier assembly operably coupled to the traction rollers, and an input element configured to transfer torque to the traction rollers.
- the input element includes a load cam and a traction ring that each has bidirectional load cam ramps.
- the transmission includes an output element configured to transfer torque from the traction rollers.
- the transmission also includes a shifter assembly configured to adjust an axis of rotation of the traction rollers.
- the transmission includes a hydraulic system operably coupled to the shifter assembly, and the transmission includes a lubrication system configured to provide lubricant to at least the traction rollers.
- Yet another aspect of the invention involves a drive having a torque converter, a main shaft coupled to the torque converter, an input load cam coupled to the main shaft, and an input traction ring operationally coupled to the input load cam.
- the drive also includes a number of traction planets adapted to receive torque from the input traction ring.
- the drive includes an output traction ring adapted to receive torque from the traction planets and an output load cam operationally coupled to the output traction ring.
- the drive also includes a planetary gearset coupled to the output load cam and to the main shaft.
- One aspect of the invention concerns a transmission having a number of spherical traction rollers, a carrier assembly for supporting the traction rollers, an input element for transferring torque to the traction rollers, and an output element for transferring torque from the traction rollers.
- the transmission includes an axial force generator for applying a clamping force to the spherical rollers, input element, and output element.
- the transmission includes a shifter assembly for adjusting an axis of rotation of the spherical traction rollers.
- the transmission includes a hydraulic system for actuating the shifter assembly, and the transmission includes a lubrication system for providing lubricant to at least the spherical traction rollers.
- CVU continuously variable unit
- the CVU includes an output traction ring in contact with the traction planets and an output load cam operationally coupled to the output traction ring.
- the CVU also includes a traction sun in contact with the traction planets.
- a number of planet axles define the axes of rotation for the traction planets.
- the CVU includes at least one shift lever for each planet axle.
- the CVU also includes at least one shift cam operationally coupled to the shift levers and at least one stator configured to axially and radially support the planet axles and the shift levers.
- the CVU includes at least one control piston configured to actuate an axial movement of the at least one shift cam, and the CVU can include a center manifold configured to support the at least one stator.
- the center manifold is also configured to provide control fluid and lubricant to the CVU.
- a continuously variable unit having a number of traction planets arranged angularly about a longitudinal axis of the CVU.
- the CVU includes a traction sun in contact with the traction planets and a number of planet axles coupled to the traction planets.
- the planet axles define the axes of rotation for the traction planets.
- the CVU includes a number of shift levers. At least one shift lever is coupled to each planet axle.
- the CVU includes a shift cam operably coupled to the shift levers, and the CVU has a stator configured to axially and radially support the planet axles and the shift levers.
- the CVU also includes at least one control piston configured to actuate an axial movement of the shift cam and a center manifold configured to support the stator.
- the center manifold is adapted to provide a control fluid and a lubricant to the CVU.
- the invention concerns a continuously variable unit (CVU) having an input element configured to receive a power input, a number of traction members coupled to the input element, a carrier assembly adapted to facilitate support of the traction members, and a load-cam-and-traction-ring subassembly configured to generate axial force.
- the CVU includes a shifter assembly operably coupled to the traction members and an output element configured to receive power from the traction members.
- the CVU includes a hydraulic system configured to be in fluid communication with the shifter assembly.
- the shifting mechanism includes a traction sun, a number of shift cams, and a number of control pistons operationally coupled to the shift cams.
- the traction sun is placed between the shift cams.
- the control piston includes a generally cylindrical body having a central bore adapted to engage a piston tube.
- the control piston includes a piston face configured to interface with control fluid and a surface configured to facilitate sensing of an axial position of the control piston.
- Another aspect of the invention relates to a control piston a control piston tube having a generally cylindrical tube with a through central bore.
- the control piston tube includes a surface adapted to couple to a control piston, and the control piston tube has a surface adapted to coupled to a shift cam.
- the shift cam includes a central bore, a shift cam profile, and a shift cam extension.
- the shift cam profile is substantially defined by the data points shown in FIG. 41 .
- the shift cam has an angled face adapted to allow lubricant flow.
- the central bore of the shift cam is adapted to couple to a control piston tube.
- the piston tube for use in a rolling traction transmission.
- the piston tube includes a substantially annular cylindrical body having a center bore, a first face located on the outer circumference of the annular cylindrical body, and a second face located on the outer circumference of the annular cylindrical body.
- the first face is configured to receive a shift cam of the transmission.
- the second face is configured to receive a control piston of the transmission.
- the piston tube also includes an orifice located on the outer circumference of the annular cylindrical body. The orifice is adapted to provide a lubricant to the transmission.
- stator-manifold assembly having a center manifold and at least one stator coupled to the center manifold so that the center manifold provides, and the stator receives, control fluid and lubricant.
- stator-manifold assembly includes at least one oil galley in fluid communication with the at least one stator.
- the center manifold for a continuously variable unit (CVU).
- the center manifold includes a base plate having a number of channels and ports for receiving and distributing control fluid and lubricant.
- the center manifold includes a cover plate adapted to couple to the base plate.
- the cover plate has a number of channels and ports for receiving and distributing control fluid and lubricant.
- the base plate for a center manifold of a continuously variable unit (CVU).
- the base plate includes a number of ports and channels for receiving and distributing fluid, and a number of recesses for clearing one or more traction planets of the CVU.
- the base plate includes one or more structures for facilitating the locating and fastening of the base plate to a housing of the CVU.
- the base plate also includes a number of channels for receiving and housing sensor cables.
- stator for a continuously variable unit (CVU).
- the stator includes a number of extensions adapted to facilitate the coupling of the stator to a manifold.
- the extensions comprise one or more channels for receiving and distributing fluid.
- the stator includes a tubular body configured to form a chamber for receiving a control fluid and a control piston.
- the stator also includes an extension configured to deliver lubricant to an oil galley.
- the invention concerns a cover plate for continuously variable unit (CVU).
- the cover plate includes a substantially circular shaped body.
- the circular shaped body has a first side face, a second side face, and a cut-out pattern configured to substantially surround an array of planet-and-shift-lever subassemblies of the CVU.
- the cover plate includes a number of lubricant channels arranged on the first side face.
- the cover plate also includes a number of lubricant spray ports positioned to be in fluid communication with the lubricant channels.
- the oil galley for a continuously variable unit (CVU).
- the oil galley includes a central bore having an annular recess for receiving fluid.
- the oil galley has a number of radial channels extending substantially radially from the annular recess toward an outer perimeter of the oil galley.
- the radial channels are spaced angularly about the central bore.
- the oil galley also includes a number of axial channels that extend substantially axially from each of the radial channels.
- One aspect of the invention relates to a transmission housing having one or more structures for retaining and locating a center manifold.
- the transmission housing includes a number of ports for delivering and receiving fluids to internal components of the transmission.
- the transmission housing includes a number of ports for receiving a number of sensors.
- the transmission housing also includes one or more passages for receiving one or more cam dowels configured to cooperate with structures of the transmission housing and/or the center manifold for retaining and locating the center manifold.
- the main shaft includes an elongated body having a first end portion, a central portion, and a second end portion.
- the main shaft includes a set of torque converter engagement splines formed on the first end portion.
- a first engagement extension extends from the torque converter engagement splines.
- the main shaft includes a set of combining device engagement splines formed on the second end portion.
- a second engagement extension extends from the second end portion.
- the main shaft includes an axial reaction flange located on the second end portion.
- the main shaft for a continuously variable transmission (CVT).
- the main shaft includes an elongated body having a first end portion, a central portion, and a second end portion.
- the main shaft includes a number of input load cam engagement splines formed on the central portion and an axial reaction flange located on the second end portion.
- the traction ring includes a substantially annular ring having a front face and a back face.
- the traction ring includes a contact surface formed on the front face.
- the traction also includes a groove formed on the back face.
- the load cam for use in a continuously variable transmission (CVT).
- the load cam includes a bowl shaped body having a perimeter edge portion and a hub portion.
- the hub portion has a central bore.
- the load cam includes a cylindrically shaped flange that is concentric with the hub portion.
- the load cam includes a number of ribs radially extending from the hub portion to the perimeter edge portion. The ribs intersect the flange.
- the load cam also includes a number of bi-directional ramps formed on a face of the perimeter edge portion.
- the input load cam shroud includes a bowl shaped body having a central opening.
- the input load cam includes several flanges formed about the perimeter of the bowl shaped body. The flanges form a number of shoulders that are adapted to engage a number of mating features of a load cam of the CVT.
- the input load cam assembly includes a load cam and a load cam shroud.
- the load cam has a bowl shaped body with a perimeter edge portion and a hub portion having a central bore.
- the load cam includes a cylindrically shaped flange concentric with the hub portion and a number of ribs extending from the hub portion to the perimeter edge portion. The ribs intersect the flange.
- the load cam also includes a number of bi-directional ramps formed on a face of the perimeter edge portion.
- the load cam shroud includes a bowl shaped body having a central opening.
- the load cam shroud also includes a number of flanges formed about the perimeter of the bowl shaped body. The flanges form a plurality of shoulders adapted to engage a plurality of mating features of a load cam shroud of the CVT.
- the invention concerns a load cam for use in a continuously variable transmission.
- the load cam includes a substantially bowl shaped body having a hub portion and a perimeter edge portion.
- the perimeter edge portion has a front face and a rear face.
- the load cam includes a number of fins arranged angularly around the front face of the perimeter edge portion.
- the load cam also includes a number of bi-directional ramps formed on a rear face of the perimeter edge portion.
- the axial lock nut for use in a continuously variable transmission (CVT).
- the axial lock nut includes a substantially cylindrical body that has a threaded central bore, an extension portion, and a polygon-shaped outer periphery portion. A number of notches are formed on the outer periphery portion. The notches are configured to couple to a dowel pin of the CVT.
- the axial lock nut also includes an anti-rock piloting surface formed on the central bore.
- the bearing support adapter for use in a continuously variable transmission (CVT).
- the bearing support adapter includes a substantially cylindrical body having a first face, a second face, and a central bore.
- the bearing support adapter has a flange extending radially from the first face. The flange is configured to react axial force.
- the bearing support adapter also includes a bearing support surface located on the outer circumference of the cylindrical body and a shoulder arranged on the central bore in proximity to the first face.
- the bearing support adapter has a thrust bearing recess formed on the second face.
- Another aspect of the invention addresses a continuously variable transmission having a main shaft, a number of spherical planets, a first load-cam-and-traction-ring subassembly, a second load-cam-and-traction-ring subassembly, and a bearing support adapter.
- the main shaft is arranged along a longitudinal axis of the transmission and adapted to receive a power input.
- the planets are arranged angularly about the longitudinal axis of the transmission.
- the first load-cam-and-traction-ring subassembly is operably coupled to the main shaft and to the spherical planets.
- the second load-cam-and-traction-ring subassembly is operably coupled to the spherical planets.
- the bearing support adapter is coupled to the main shaft and configured to support a bearing coupled to the second load-cam-and-traction-ring subassembly.
- the shift-cam-and-sun subassembly for a continuously variable transmission (CVT).
- the shift-cam-and-sun subassembly includes a traction sun, a shift cam operably coupled to the traction sun, and a piston tube coupled to the shift cam.
- the piston tube is coaxial with the traction sun.
- the shift-cam-and-sun subassembly also includes a control piston coupled to the piston tube.
- the control piston is coaxial with the traction sun.
- the traction sun for a continuously variable transmission (CVT).
- the traction sun includes a generally cylindrical body having a central bore.
- a first recess is formed on the central bore, and is configured to receive a bearing.
- a central shoulder is formed on the central bore, and is in proximity to the first recess.
- the traction sun also includes an exterior edge face formed on the outer circumference of the cylindrical body. The exterior edge face configured to be a rolling contact surface for number of traction planets of the CVT.
- the shift cam for a continuously variable transmission (CVT).
- the shift cam includes a substantially disc-shaped body having a front face, a rear face, and a central bore.
- the shift cam has an extension surface extending from the central bore.
- the shift cam has a reference surface formed on the rear face.
- the shift cam also has a shift cam profile formed on the front face.
- a set of coordinates define the shape of the shift cam profile. The coordinates are based on the reference surface and include those of the data table shown in FIG. 41 .
- cam dowel having a substantially cylindrical body with a central bore, a first end portion, and a second end portion.
- the cam dowel includes a cam wedge formed on the first end portion.
- the cam dowel also includes a substantially flat face formed on the second end portion.
- the combining device includes a transfer shaft, a hub, a number of planet gears, a planet gear carrier, and a sun gear.
- the transfer shaft is an elongated body with a first end, a second end, and a central bore.
- the hub is operably coupled to the transfer shaft and is coaxial with the transfer shaft.
- the planet gears are operably coupled to the hub.
- the planet gear carrier is configured to support the planet gears.
- the sun gear is coupled to the planet gears.
- the sun gear has a central bore configured to couple to a main axle of the CVT.
- the invention concerns a combining device for use in a continuously variable transmission (CVT).
- the combining device includes a hub configured to support a planetary gear set.
- the combining device has a first power input portion operably coupled to the hub.
- the hub has a second power input portion.
- the combining device also has a power output portion operably coupled to the hub.
- the transmission includes a variator having a number of traction planets arranged angularly about the longitudinal axis of the transmission.
- the transmission includes a combining device operably coupled to the variator and to the main shaft.
- the transmission also includes a rangebox operably coupled to the combining device.
- the rangebox includes a power input portion configured to receive power from a transfer shaft of the CVT, and an output shaft arranged along the longitudinal axis of the rangebox.
- the output shaft is configured to transfer power out of the rangebox.
- the rangebox includes a high-and-low mode subassembly configured to receive power from the power input portion.
- the high-and-low mode subassembly is arranged along the longitudinal axis of the range box and coaxial with the output shaft.
- the rangebox includes a reverse mode subassembly configured to receive power from the power input portion.
- the reverse mode subassembly is operably coupled to the output shaft.
- the rangebox also includes an overrun clutch operably coupled to the high-and-low mode subassembly and arranged between the forward clutch and the power input portion.
- the planet axle for supporting rotation of a traction roller and facilitating a tilting of the axis of rotation.
- the planet axle includes a generally cylindrical body having a through bore along a longitudinal axis of the cylindrical body.
- the planet axle also includes one or more axle capturing features for engagement of a transverse axle.
- the shift lever for a continuously variable transmission (CVT).
- the shift lever has an elongated body with a first end portion and a second end portion.
- the shift lever includes a first bore formed on the first end portion.
- the first bore is configured to receive a planet axle of the CVT.
- the shift lever has a second bore formed on the first end portion.
- the second bore intersects the first bore in a substantially perpendicular location.
- the second bore is configured to receive a shift guide roller axle of the CVT.
- the shift lever also has an axle receiving passage formed on the second end.
- the axle receiving passage is configured to receive a shift cam roller axle of the CVT.
- the planet-and-shift-lever mechanism includes a spherical planet having a central bore, a planet axle placed in the central bore, and a first shift lever coupled to a first end of the planet axle.
- the planet-and-shift-lever mechanism has a second shift lever coupled to a second end of the planet axle and a first skew roller coupled to the first end of the planet axle.
- the planet-and-shift-lever mechanism also has a second skew roller coupled to the second end of the planet axle, a first shift cam roller coupled to the first shift lever, and a second shift cam roller coupled to the second shift lever.
- FIG. 1 is a high-level block diagram showing an embodiment of a drive apparatus 100 that includes an inventive continuously variable transmission and continuously variable unit.
- FIG. 2 is a schematic diagram of one embodiment of continuously variable transmission and continuously variable unit in accordance with certain inventive teachings of the disclosure.
- FIG. 3A is a cross-sectional view of one embodiment of a continuously variable transmission employing a continuously variable unit.
- FIG. 3B is a partially exploded view of the continuously variable transmission of FIG. 3A .
- FIG. 4 is a partial cross-section of certain components of a continuously variable unit (CVU).
- CVU continuously variable unit
- FIG. 5 is a perspective view of a shaft that can be used with the CVU of FIG. 4 .
- FIG. 6 is a cross-sectional view of the shaft of FIG. 5 .
- FIG. 7 is a partial cross-section of certain components of the CVU of FIG. 4 .
- FIG. 8 is a perspective view of a traction ring that can be used with the CVU of FIG. 4 .
- FIG. 9 is a cross-sectional view of the traction ring of FIG. 8 .
- FIG. 10 is a perspective view of a load cam and shroud assembly that can be used with the CVU of FIG. 4 .
- FIG. 11 is a perspective view of the load cam and shroud assembly of FIG. 10 .
- FIG. 12 is a partially exploded view of the load cam and shroud assembly of FIG. 10 .
- FIG. 13 is a perspective view of a load cam that can be used with the CVU of FIG. 4 .
- FIG. 14 is a cross-sectional view of the load cam of FIG. 13 .
- FIG. 15 is a perspective view of a lock nut that can be used with the CVU of FIG. 4 .
- FIG. 16 is a cross-sectional view of the lock nut of FIG. 15 .
- FIG. 17 is a perspective view of yet another load cam that can be used with the CVU of FIG. 4 .
- FIG. 18 is yet another perspective of the load cam of FIG. 17 .
- FIG. 19 is a cross-sectional view of the load cam of FIG. 17 .
- FIG. 20 is a partial cross-section of certain components of the CVU of FIG. 4 .
- FIG. 21 is a perspective view of yet another load cam that can be used with the CVU of FIG. 4 .
- FIG. 22 is a cross-sectional view of the load cam of FIG. 21 .
- FIG. 23 is another perspective view of the load cam of FIG. 21 .
- FIG. 24 is a perspective view of a shroud that can be used with the CVU of FIG. 4 .
- FIG. 25 is a perspective view of a bearing support adapter that can be used with the CVU of FIG. 4 .
- FIG. 26 is a cross-sectional view of the bearing support adapter of FIG. 25 .
- FIG. 27 is a perspective view of yet another load cam that can be used with the CVU of FIG. 4 .
- FIG. 28 is another perspective view of the load cam of FIG. 27 .
- FIG. 29 is a cross-sectional view of the load cam of FIG. 27 .
- FIG. 30 is a partial cross-sectional view of certain components of the CVU of FIG. 4 .
- FIG. 31 is a perspective view of a planet-and-shift-lever subassembly that can be used with the CVU of FIG. 4 .
- FIG. 32 is a cross-sectional view of certain components of the planet-and-shift-lever subassembly of FIG. 31 .
- FIG. 33 is an exploded view of the planet-and-shift-lever-subassembly of FIG. 32 .
- FIG. 34 is a perspective view of a planet axle that can be used with the CVU of FIG. 4 .
- FIG. 35 is a cross-sectional view of the planet axle of FIG. 34 .
- FIG. 36 is a perspective view of a shift-cam-and-sun subassembly that can be used with the CVU of FIG. 4 .
- FIG. 37 is a cross-sectional view of certain components of the shift-cam-and-sun subassembly of FIG. 36 .
- FIG. 38 is an explode view of certain components of the shift-cam-and-sun subassembly of FIG. 37 .
- FIG. 39 is a cross-sectional view of a sun that can be used with the CVU of FIG. 4 .
- FIG. 40 is a cross-sectional view of a shift cam that can be used with the CVU of FIG. 4 .
- FIG. 40A is a detail view A of the shift cam of FIG. 40 .
- FIG. 41 is a data table with data points specifying a suitable profile for the shift cam of FIG. 40 .
- FIG. 42 is a cross-sectional view of a control piston that can be used with the CVU of FIG. 4 .
- FIG. 43 is a perspective view of a piston tube that can be used with the CVU of FIG. 4 .
- FIG. 44 is a partial, cross-sectional view of certain components of the CVU of FIG. 4 .
- FIG. 45 is a perspective view of a stator-manifold subassembly that can be used with the CVU of FIG. 4 .
- FIG. 46 is a cross-sectional view of certain components of the stator-manifold of FIG. 45 .
- FIG. 47 is a perspective view of a center manifold that can be used with the stator-manifold of FIG. 45 .
- FIG. 48 is a second perspective view of the center manifold of FIG. 47 .
- FIG. 49 is a perspective view of a base plate that can be used with the center manifold of FIG. 47 .
- FIG. 50 is a second perspective view of the base plate of FIG. 49 .
- FIG. 51A and FIG. 51B are perspective views of a cam dowel that can be used with the CVU of FIG. 4 and the stator-manifold subassembly of FIG. 45 .
- FIG. 52 is a plan view of a cover plate that can be used with the center manifold of FIG. 47 .
- FIG. 53 is a perspective view of the cover plate of FIG. 52 .
- FIG. 54 is a perspective view of a stator that can be used with the CVU of FIG. 4 .
- FIG. 55 is a second perspective view of the stator of FIG. 54 .
- FIG. 56 is a cross-sectional view of the stator of FIG. 54 .
- FIG. 57 is yet another cross-sectional view of the stator of FIG. 54 .
- FIG. 58 is yet another cross-sectional view of the stator of FIG. 54 .
- FIG. 59 is side view of the stator of FIG. 54 .
- FIG. 60 is a perspective view of an oil galley that can be used with the CVU of FIG. 4 .
- FIG. 61 is a second perspective view of the oil galley of FIG. 60 .
- FIG. 62 is a cross-sectional view of the oil galley of FIG. 60 .
- FIG. 63 is a partial, cross-sectional view of certain components of the CVU of FIG. 4 .
- FIG. 64 is a yet another cross-sectional view of certain components of the CVU of FIG. 4 .
- FIG. 65 is a perspective view of a bell housing and certain components of an input interface that can be used with transmissions of FIGS. 1 , 2 , and 3 A.
- FIG. 66 is a cross-sectional, partial perspective view of the bell housing of FIG. 65 .
- FIG. 67 is a partially explode view of certain components of the bell housing and input interface of FIG. 65 .
- FIG. 68 is a perspective view of a combining device that can be use with the transmission o FIG. 3A .
- FIG. 69 is a side view of the combining device of FIG. 68 .
- FIG. 70 is a cross-sectional view of the combining device of FIG. 68 .
- FIG. 71 is a partially exploded view of certain components of the combining device of FIG. 67 .
- FIG. 72 is a schematic diagram of a continuously variable unit adapted to cooperate with a rangebox.
- FIG. 73 is a perspective view of one embodiment of a range box that can be used with the CVU of FIG. 4 and/or the transmission of FIG. 3A .
- FIG. 74 is a cross-sectional view of the rangebox of FIG. 73 .
- FIG. 75 is a perspective view of a rear housing that can be used with the transmission of FIG. 3A .
- FIG. 76 is a cross-sectional, perspective view of certain components and features of the rear housing of FIG. 75 .
- FIG. 77 is a plan view of the bottom side of the rear housing of FIG. 75 .
- the terms “operationally connected,” “operationally coupled”, “operationally linked”, “operably connected”, “operably coupled”, “operably linked,” and like terms refer to a relationship (mechanical, linkage, coupling, etc.) between elements whereby operation of one element results in a corresponding, following, or simultaneous operation or actuation of a second element. It is noted that in using said terms to describe inventive embodiments, specific structures or mechanisms that link or couple the elements are typically described. However, unless otherwise specifically stated, when one of said terms is used, the term indicates that the actual linkage or coupling may take a variety of forms, which in certain instances will be obvious to a person of ordinary skill in the relevant technology.
- radial is used here to indicate a direction or position that is perpendicular relative to a longitudinal axis of a transmission or variator.
- axial refers to a direction or position along an axis that is parallel to a main or longitudinal axis of a transmission or variator.
- FIG. 1 is a high-level block diagram showing an embodiment of a drive apparatus 100 , which is referred to herein as the drive 100 .
- the drive 100 includes a transmission 101 operationally coupled between a prime mover 102 and a load 114 .
- the prime mover 102 delivers power to the transmission 101
- the transmission 101 delivers power to the load 114 .
- the prime mover 102 can be one or more of any number of power generating devices
- the load 114 can be one or more of any number of driven devices or components. Examples of the prime mover 102 include, but are not limited to, engines, motors and the like. Examples of loads include, but are not limited to, drivetrain differential assemblies, power take-off assemblies, generator assemblies, pump assemblies, and the like.
- the transmission 101 includes an input interface 104 , a variator 106 , a parallel branch 108 (for example, a fixed ratio branch), an output interface 110 , and a rangebox 112 .
- the input interface 104 is operationally coupled to the prime mover 102 .
- the variator 106 and the parallel branch 108 can be operationally coupled in parallel between the input interface 104 and the output interface 110 .
- the rangebox 112 is operationally coupled between the output interface 110 and the load 114 .
- the input interface 104 can be configured for receiving power from the prime mover 102 and transferring such power to the variator 106 and the parallel branch 108 in a distributed manner.
- the output interface 110 can be configured for combining power (that is, torque applied at a given rotational speed) from the variator 106 and the parallel branch 108 and transferring such combined power to the rangebox 112 . It is disclosed herein that neither the input interface 104 nor the output interface 110 is necessarily limited to a particular respective physical and/or operational configuration. Accordingly, the input interface 104 may include any gearing or coupling structure suitable for providing such distributed power transfer and distribution functionality, and the output interface 110 may include any gearing or coupling structure suitable for providing such combined power transfer functionality. Examples of the input interface 104 include, but are not limited to, a torque converter assembly, a hydraulic clutch coupling, a manually actuated clutch assembly, a computer-controlled clutch assembly, a magnetorheological clutch coupling, and the like.
- the parallel branch 108 can be configured for enabling power distributed thereto from the input interface 104 to be directly transferred to the output interface 110 without any selective variation (that is, adjustment) of rotational speed and/or rotational direction associated with that power.
- the parallel branch 108 can be configured to modulate power in discrete (that is, stepped) or continuously variable modes.
- the variator 106 can be configured for enabling power distributed thereto from the input interface 104 to be transferred to the output interface 110 in a manner whereby torque and/or rotational speed associated with that power is selectively variable (that is, selectively adjustable).
- a torque split unit in accordance with one embodiment of the present invention comprises the variator 106 and the parallel branch 108 and provides for two power paths between the input interface 104 and the output interface 110 .
- a first one of the power paths extends through the variator 106 and a second one of the power paths extends through the parallel branch 108 .
- power distribution between the two power paths is dependent upon a selectively variable ratio of an input power specification of the variator 106 (for example, input torque and input rotational shaft speed) with respect to an output power specification of the variator 106 (for example, output torque and output rotational shaft speed).
- an input power specification of the variator 106 for example, input torque and input rotational shaft speed
- an output power specification of the variator 106 for example, output torque and output rotational shaft speed
- a transmission in accordance with the present invention is of a split torque type.
- the parallel branch 108 may, in some embodiment of the present invention, be omitted such that power is transferred between the input interface 104 and the output interface 110 solely through the variator 106 .
- the rangebox 112 provides various gear selection and clutch engagement functionalities.
- gear selection functionality include, but are not limited to, selective engagement of available rangebox gear ratios and selective engagement of various load drive directions.
- clutch engagement functionality include, but are not limited to, passive implementation of various clutch engagement operations and active implementation of various clutch engagement operations.
- the input interface 104 can serve as a torque interface for receiving an applied input torque at a given rotational speed or range of rotational speeds from the prime mover 102 .
- the applied input torque is delivered to the variator 106 and the parallel branch 108 in a distributed manner. Torque is distributed dependent upon a torque ratio setting of the variator 1200 .
- the parallel branch 108 can be configured to receive power from the input interface 104 and to distribute that power directly to the output interface 110 without any selective variation of rotational speed and/or rotational direction associated with that power.
- the parallel branch 108 includes a shaft rotatably coupled between the input interface 104 and the output interface 110 for transferring power from the input interface 104 and the output interface 110 without any selective variation of rotational speed and/or rotational direction associated with that power.
- the variator 106 can include traction members 202 , an input element 204 , a shifter assembly 206 , an axial force generator (AFG) 208 , a carrier assembly 210 , a hydraulic system 212 , a lubrication system 214 , and an output element 216 .
- the input element 204 , the shifter assembly 206 , the axial force generator 208 , the carrier assembly 210 , the lubrication system 214 , and the output element 216 are operationally coupled to the traction members 202 .
- the hydraulic system 212 is operationally connected to the shifter assembly 206 and is configured for adjusting a torque ratio setting of the variator 106 .
- the input element 204 is operationally coupled to the input interface 104 for receiving power from the input interface 104 . Power is transmitted from input element 204 to the output element 216 through the traction members 202 . Power is output from the variator 106 through the output element 216 , being delivered to the output interface 110 .
- the carrier assembly 210 provides for physical placement and support of the traction members 202 .
- the shifter assembly 206 provides functionality for selectively manipulating the traction members 202 , thereby enabling a ratio of input torque exerted on the input element 204 to output torque exerted on the output element 216 (that is, the torque ratio) to be selectively varied in a continuous, or stepless, manner. In doing so, the shifter assembly 206 enables the amount of torque transferred jointly by the variator 106 and the parallel branch 108 between the input interface 104 and the output interface 110 to be selectively varied.
- the hydraulic system 212 can be configured for hydraulically controlling the shifter assembly 206 to vary the torque ratio.
- the lubrication system 214 can be configured to deliver a lubricant to, among other things, mechanical interfaces between traction members 202 , the input element 204 , and the output element 216 .
- the lubrication system 214 is adapted to provide lubricant to the rangebox 112 .
- the axial force generator 208 can be configured for exerting a force (for example, clamping force, axial force, etc.) to keep the input element 204 and the output element 216 in sufficient contact with the traction members 202 , thereby limiting slippage at points of contact therebetween.
- the axial force generator 208 can cooperate with, or be at least partly operationally coupled with the hydraulic system 212 .
- the rangebox 112 includes a first rangebox structure 220 configured for varying a gear range, a second rangebox structure 222 configured for adjusting a load drive direction, and a third rangebox structure 224 configured to protect against load overrun conditions.
- the first rangebox structure 220 preferably facilitates selective adjustment between a rangebox high gear ratio (for example, relatively low torque output exerted at a relatively high rotational speed) and a rangebox low gear ratio (for example, relatively high torque output exerted at a relatively low rotational speed), which increases the overall gear ratio range of the transmission 101 .
- the second rangebox structure 222 can be configured to facilitate selective adjustment between a first rotary drive direction (for example, corresponding to driving the load 114 in a forward operational direction) and a second rotary drive direction (for example, corresponding to driving the load 114 in a reverse operational direction).
- the third rangebox structure 224 is adapted to facilitate mechanical slippage in the case where the load 114 attempts to back drive the prime mover 102 through the transmission 101 .
- the transmission 600 can include a torque converter subassembly 800 , a main shaft 1000 , a variator 1200 , a combining device 1400 , a rangebox 1600 , and a transmission housing 1800 .
- the transmission housing 1800 can include a bell housing 1810 (that is, a first housing portion) and a rear housing 1820 (that is, a second housing portion) separably connected to the bell housing 1810 .
- the torque converter subassembly 800 , the main shaft 1000 , the variator 1200 , the combining device 1400 , and the rangebox 1600 are operably mounted on or within the transmission housing 1800 in an axially aligned manner.
- the transmission housing 1800 is configured for housing and supporting various subassemblies and/or components of the transmission 600 .
- any one of the torque converter subassembly 800 , the variator 1200 , the combining device 1400 , and the rangebox 1600 can be arranged in a parallel shaft configuration relative to the other components.
- the variator 1200 and the main shaft 1000 can be operably coupled between a power output portion of the torque converter subassembly 800 and power input portions of the combining device 1400 .
- the torque converter subassembly 800 transfers power to the variator 1200 through the main shaft 1000 .
- the variator 1200 supplies power to a first power input portion 1410 of the combining device 1400 .
- the main shaft 1000 supplies power to a second power input portion 1405 of the combining device 1400 .
- Power from the variator 1200 and the main shaft 1000 can be supplied to the combining device 1400 in a selectively variable ratio (for example, power from the variator 1200 in relation to power from the main shaft 1000 ) and can be combined by the combining device 1400 .
- the combining device 1400 delivers the combined power to the rangebox 1600 via a power output portion 1401 of the combining device 1400 .
- the power output portion 1401 can include a carrier of planetary gear set and/or a transfer shaft.
- the variator 1200 mounts on the main shaft 1000 .
- the variator 1200 and the main shaft 1000 form a torque split unit. More specifically, the ratio of torque transferred to the combining device 1400 through the variator 1200 or through the main shaft 1000 is selectively variable dependent upon a torque ratio setting of the variator 1200 .
- the variator 1200 transfers power to the combining device 1400 in a manner whereby the torque and/or the rotational speed associated with that power is selectively and continuously variable (that is, adjustable).
- the variator 1200 can be configured for receiving power of a first specification (for example, first torque and first rotational shaft speed) and outputting power of a second specification (for example, second torque and second rotational shaft speed).
- the torque converter subassembly 800 is one embodiment of an input interface 104 , for example, thereby providing the functionality of transferring power from a prime mover attached to the torque converter subassembly 800 to the variator 1200 via, for example, the main shaft 1000 .
- a different type of input interface such as, for example, a manually controlled clutch subassembly, a computer controlled clutch assembly, or a flywheel can be implemented in place of the torque converter subassembly 800 .
- the combining device 1400 is an embodiment of an output interface, thereby providing the functionality of combining power received from the variator 1200 and the main shaft 1000 and transferring such power to the rangebox 1600 .
- the rangebox 1600 receives power from the combining device 1400 and outputs power in conjunction with providing one or more of the various gear selection and clutch engagement functionalities discussed above in reference to FIGS. 1 and 2 .
- the rangebox 1600 in combination with the variator 1200 enables the transmission 600 to operate in multiple modes (that is, a multi-mode transmission).
- the variator 1200 can include an input load-cam-and-traction-ring subassembly 2000 A, an output load-cam-and-traction-ring subassembly 2000 B, an array of planet-and-shift-lever subassemblies 2100 , a shift-cam-and-sun subassembly 2200 , and a stator-manifold subassembly 2300 .
- the shift-cam-and-sun subassembly 2200 is supported by the stator-manifold subassembly 2300 .
- the shift-cam-and-sun subassembly 2200 is supported in a manner enabling the shift-cam-and-sun subassembly 2200 to be translated along a longitudinal axis LA 1 of the main shaft 1000 .
- the planet-and-shift-lever subassemblies 2100 are arrayed angularly around the main shaft 1000 , and are supported jointly by the shift-cam-and-sun subassembly 2200 and the stator-manifold subassembly 2300 .
- Each one of the planet-and-shift-lever subassemblies 2100 is supported in a manner that facilitates synchronous rotation of all the planet-and-shift-lever subassemblies 2100 about a respective reference axis TA 1 extending through a planet 2102 of each one of the planet-and-shift-lever subassemblies 2100 .
- a respective reference axis TA 1 extending through a planet 2102 of each one of the planet-and-shift-lever subassemblies 2100 .
- the axis TA 1 see FIG.
- each one of the planet-and-shift-lever subassemblies 2100 extends through a center point of the respective planet 2102 substantially perpendicular to a radial reference axis RA 1 extending from the longitudinal axis LA 1 through the center point of the respective planet 2102 .
- the main shaft 1000 includes a first end portion 1005 , a central portion 1010 and a second end portion 1015 .
- the first end portion 1005 couples to a power output portion 805 of the torque converter assembly 800 (for example, an output hub of a converter turbine) in a manner precluding relative rotation of the main shaft 1000 with respect to the power output portion 805 .
- the central portion 1010 of the main shaft 1000 couples to the input load-cam-and-traction-ring subassembly 2000 A in a manner precluding relative rotation of the main shaft 1000 with respect to the input load-cam-and-traction-ring subassembly 2000 A.
- the second end portion 1015 of the main shaft 1000 couples to the first power input portion 1405 of the combining device 1400 in a manner precluding relative rotation of the main shaft 1000 with respect to the first power input portion 1405 .
- the output load-cam-and-traction-ring subassembly 2000 B of the variator 1200 couples to a second power input portion 1410 of the combining device 1400 in a manner precluding relative rotation of the output load-cam-and-traction-ring subassembly 2000 B with respect to the second power input portion 1410 .
- the main shaft 1000 is suitably configured for transferring power from the torque converter subassembly 800 (a) directly to the combining device 1400 , and (b) to the combining device 1400 through the variator 1200 .
- Each of the planets 2102 is located by the input load-cam-and-traction-ring subassembly 2000 A, the output load-cam-and-traction-ring subassembly 2000 B, and the shift-cam-and-sun subassembly 2200 .
- the main shaft 1000 can be configured to exert torque on the input load-cam-and-traction-ring subassembly 2000 A.
- the input traction interface TI 1 is defined, as used here, at a region of contact between the input load-cam-and-traction-ring subassembly 2000 A and the respective planet 2102 .
- the output traction interface TI 2 is defined, as used here, at a region of contact between the output load-cam-and-traction-ring subassembly 2000 B and the respective planet 2102 .
- the output load-cam-and-traction-ring subassembly 2000 B can be coupled to the combining device 1400 . Accordingly, torque can be transferred from the main shaft 1000 to the combining device 1400 through the variator 1200 .
- the ratio of torque transferred to the combining device 1400 through the variator 1200 or through the main shaft 1000 can be selectively variable dependent upon the torque ratio of the variator 1200 .
- the torque ratio refers to a relative position of the input traction interface TI 1 and the output traction interface TI 2 , relative to the axis LA 2 , for a given tilt of the planet-and-shift-lever subassemblies 2100 .
- the torque ratio is substantially equal to 1 and there is no corresponding torque multiplication.
- the ratio of the tangential surface velocity of the planets 2102 at the input traction interface TI 1 to that of the tangential surface velocity of the planets 2102 at the output traction interface TI 2 is selectively adjustable.
- the shift-cam-and-sun subassembly can be configured such that translation of the shift-cam-and-sun subassembly 2200 causes such tilt of the planet-and-shift-lever subassemblies 2100 .
- the direction of tilt of the planet-and-shift-lever subassemblies 2100 from the position corresponding to the torque ratio of 1 dictates whether the torque multiplication is greater than 1 (that is, torque output is greater than torque input) or less than 1 (that is, torque input is greater than torque output).
- the input traction interface TI 1 and the output traction interface TI 2 are angularly equidistant relative to a radial reference axis RA 1 extending through the tangential reference axis TA 1 .
- the torque ratio is 1 when a longitudinal axis LA 2 of each planet 2102 is parallel with the longitudinal axis LA 1 of the main shaft 1000 .
- Such an equidistant configuration provides for a balanced adjustment range such that full adjustment of the planet-and-shift-lever subassemblies 2100 in a first adjustment direction results in the same absolute torque multiplication value as full adjustment in a second direction.
- the input traction interface TI 1 and the output traction interface TI 2 may be non-equidistant from the reference axis TA 1 when the torque ratio is 1.0 and the longitudinal axis LA 2 is parallel with the longitudinal axis LA 1 .
- Such a non-equidistant configuration provides for biasing of the adjustment range such that full adjustment of the planet-and-shift-lever subassemblies 2100 in the first adjustment direction results in a different absolute torque multiplication value than full adjustment in the second adjustment direction.
- the variator 1200 can be axially constrained on the main shaft 1000 between an axial reaction flange 1020 of the main shaft 1000 and an axial lock nut 1305 ( FIG. 4 ).
- the axial lock nut 1305 includes a threaded bore configured for mating with a corresponding threaded portion 1025 of the main shaft 1000 .
- the axial reaction flange 1020 can be fixedly attached to the main shaft 1000 adjacent the second end portion 1015 of the main shaft 1000 .
- the threaded portion 1025 can be an integral component of the main shaft 1000 , adjacent to the central portion 1010 of the main shaft 1000 .
- the main shaft 1000 includes an anti-rock piloting surface 1028 configured for engaging a mating anti-rock piloting surface of the axial lock nut 1305 for limiting rocking of the axial lock nut 1305 with respect to the main shaft 1000 .
- a first engagement extension 1030 at the first end portion 1005 of the main shaft 1000 can be configured for engaging or supporting a bearing assembly 810 ( FIG. 3A ) that interfaces with certain components of the torque converter subassembly 800 or other support member.
- a second engagement extension 1035 at the second end portion 1015 of the main shaft 1000 can be configured for engaging or supporting a bearing assembly 1415 ( FIG. 3A ) that interfaces with certain components of the combining device 1400 .
- the bearing assemblies 810 , 1415 include each only a bushing or a bearing component.
- the bearing assemblies 810 , 1415 each include a bushing or a bearing component and a seal component configured to engage a mating surface of the respective engagement extension 1030 , 1035 .
- the first end portion 1005 of the main shaft 1000 can include torque converter engaging splines 1040 configured to couple to mating splines of the power output hub of the torque converter assembly 800 .
- the central portion 1010 of the main shaft 1000 includes input load cam engaging splines 1045 configured to couple to mating splines of the input-load-and-traction-ring subassembly 2000 A (that is, a power input portion) of the variator 1200 .
- the second end portion 1015 of the main shaft 1000 can include combining device engaging splines 1050 configured to couple to mating splines of the first power input portion 1405 of the combining device 1400 .
- the main shaft 1000 can be configured for transferring power from the torque converter subassembly 800 directly to the combining device 1400 , and to the combining device 1400 through the variator 1200 .
- a splined coupling is one example of a coupling suitable for precluding relative rotation of the main shaft 1000 with respect to the power output portion of the torque converter subassembly 800 , the power input portion of the variator 1200 , and the first power input portion 1405 of the combining device 1400 .
- other couplings can be used.
- a key and mating engagement coupling is another example of a suitable coupling.
- the main shaft 1000 can include a first channel 1055 ( FIGS. 3A , 4 and 6 ) for facilitating flow of a transmission fluid from the power output portion 805 of the torque converter subassembly 800 to an interface between the main shaft 1000 a transmission oil pump 806 ( FIG. 3A ) of the torque converter subassembly 800 .
- the main shaft 1000 can include a second channel 1060 for enabling flow of lubricant to the variator 1200 and/or to the combining device 1400 .
- the input load-cam-and-traction-ring subassembly 2000 A can include an input load cam 2005 A, an input traction ring 2010 A, a plurality of input load cam rollers 2015 A ( FIG. 7 ), and an input load cam shroud 2020 A.
- the input load cam 2005 A is in splined engagement with the main shaft 1000 , thereby facilitating the transfer of torque from the main shaft 1000 to the input load cam 2005 A.
- the input load cam 2005 A can be configured to transfer torque to an input traction ring 2010 A via the plurality of input load cam rollers 2015 A.
- the input load cam rollers 2015 A are engaged between the input load cam 2005 A and the input traction ring 2010 A.
- the input traction ring 2010 A can be positioned between the input load cam rollers 2015 A and the planets 2102 . Torque applied to the input load cam 2005 A by the main shaft 1000 is transferred from the input load cam 2005 A to the input traction ring 2010 A through the load cam rollers 2015 A.
- the input load cam 2005 A can include a generally bowl-shaped body 2052 A (see FIGS. 10-11 ) having a hub portion 2054 A and a perimeter edge portion 2056 A.
- the hub portion 2054 A includes a central bore 2058 A having internal splines configured for mating with the input load cam engaging splines 1045 ( FIG. 5 ) of the main shaft 1000 , thereby supporting the input load cam 2005 A and enabling power to be transferred from the main shaft 1000 to the variator 1200 .
- a set of bi-directional ramps 2060 A can be provided in a rear face 2062 A of the perimeter edge portion 2056 A.
- the ramps 2060 A can be configured for receiving one of the input load cam rollers 2015 A ( FIG. 7 ) and cooperates with the respective input load cam roller 2015 A for applying an axial force and a tangential force on the input traction ring 2010 A.
- a cam roller retainer (not shown) can be provided to receive and support the input load cam rollers 2015 .
- rotation of the input load cam 2005 A causes the input load cam rollers 2015 A to urge the input traction ring 2010 A into compressive engagement with the planets 2102 and to urge the input traction ring 2010 A into rotation about the longitudinal axis LA 1 of the main shaft 1000 , thereby providing for torque transfer from the input load cam 2005 A to the planets 2102 via the input traction ring 2010 A.
- the input traction ring 2010 A has a generally annular ring shape with a front face 2061 A and a back face 2063 A.
- the input traction ring 2010 A includes a contact surface 2065 A that engages the planets 2102 (one shown in FIG. 7 ).
- the input traction interface TI 1 is the region of contact between the contact surface 2065 A of the input traction ring 2010 A and each one of the planets 2102 (one shown in FIG. 7 ).
- torque imparted to the input traction ring 2010 A by the input load cam 2005 A is transferred to the planets 2102 , thereby causing each planet 2102 to rotate about the respective planet axle 2104 .
- traction at each input traction interface TI 1 is provided through an elastohydrodynamic layer formed by a traction fluid.
- the contact surface 2065 A is generally angled relative to the front face 2061 A, such that the profile of the contact surface 2065 A mates efficiently with a curvature of each planet 2102 .
- the angle of inclination between the front face 2061 A and the contact surface 2065 A can be between about 5 degrees and 75 degrees, more preferably between about 15 degrees and 65 degrees, even more preferably between about 30 degrees and 55 degrees, and most preferably between about 35 degrees and 50 degrees.
- the back face 2063 A can include a radiused groove 2067 A configured for receiving the load cam rollers 2015 A to facilitate torque transfer from the input load cam 2005 A to the input traction ring 2010 A. It is disclosed herein that an input traction ring can include the set of bi-directional ramps, and an input load cam can include the radiused groove. In other embodiments, the input traction ring and the input load cam both have ramps.
- radially extending ribs 2064 A can be attached to a front face 2066 A of the body 2052 A, extending generally from the perimeter edge portion 2056 A to the hub portion 2054 A.
- a cylindrically shaped flange 2068 A extends from the front face 2066 A.
- the cylindrically shaped flange 2068 A intersects the radially extending ribs 2064 A.
- the radially extending ribs 2064 A and the cylindrically shaped flange 2068 A jointly and individually enhance stiffness of the bowl-shaped body 2052 A and serve as cooling fins for dissipating heat.
- the radially extending ribs 2064 A can be used to facilitate the sensing of rotational speed of the input load cam 2005 A.
- a recess 2070 A in a front face 2071 A of the hub portion 2054 A is configured for receiving an anti-rocking device 2072 A ( FIG. 12 ) such as, for example, a bushing, a bearing or a sleeve, which serves to limit rocking of the input load cam 2005 A with respect to the main shaft 1000 .
- a preloading spring recess 2076 A and a thrust bearing recess 2078 A are provided in a rear face 2079 A of the hub portion 2054 A.
- the preload spring recess 2076 A is configured for receiving a preloading spring 2083 A ( FIG.
- such a preloading spring and thrust bearing arrangement serves to exert a reactive preload force between the input load cam assembly 2000 A, the stator-manifold subassembly 2300 and the output load cam assembly 2000 B when the preloading spring 2083 A is compressed.
- the preloading spring 2083 A include, but are not limited to, a Bellville washer, a wavy washer, a helical compression spring and other suitably configured spring members.
- the thrust bearing 2085 A include, but are not limited to, a roller thrust bearing, a thrust bushing, and other devices suitably configured for carrying a thrust load.
- a plurality of dowel pin holes 2069 A ( FIGS. 12 and 14 ) in the front face 2071 A can be configured for receiving one or more dowel pins (not shown) to facilitate coupling of the axial lock nut 1305 ( FIGS. 7 , 15 and 16 ) to the input load cam 2005 A for preventing unintentional loosening of the axial lock nut 1305 .
- the axial lock nut 1305 can have a threaded bore 1306 configured for engaging the corresponding threaded portion 1025 of the main shaft 1000 .
- the axial lock nut 1305 can be provided with a polygonal-shaped (for example, hexagonal) outer periphery portion 1307 configured to engage a tool for manipulating the axial lock nut 1305 .
- a plurality of notches 1309 can be provided in the outer periphery portion 1307 for engaging dowels (not shown) received within one of the dowel pin holes 2069 A.
- Such engagement facilitates selective angular positioning and constraining of the axial lock nut 1305 with respect to the load input cam 2005 A, which is useful for preventing unintentional loosening of the axial lock nut 1305 .
- a circumferential groove 1311 exposed at an exterior surface 1312 of the axial lock nut 1305 can be configured to receive a retaining device (not shown) such as, for example, a snap ring to retain the one or more dowels within respective ones of the dowel pin holes 2069 A.
- a retaining device such as, for example, a snap ring to retain the one or more dowels within respective ones of the dowel pin holes 2069 A.
- the retaining device prevents the dowels from unintentionally backing out of the respective dowel pin holes 2069 A.
- An extension portion 1313 of the axial lock nut 1305 includes an anti-rock piloting surface 1315 (that is, a reaction surface) that engages the mating anti-rock piloting surface 1028 ( FIG. 5 ) of the main shaft 1000 for limiting rocking of the axial lock nut 1305 with respect to the main shaft 1000 .
- the input load cam shroud 2020 A includes a bowl-shaped body 2082 A having perimeter flanges 2084 A.
- the input load cam shroud 2020 A is mountable over the front face 2066 A of the input load cam 2005 A.
- each one of the perimeter flanges 2084 A can be positioned between a respective adjacent pair of the radially extending ribs 2064 A, and the hub portion 2054 A is exposed within a central opening 2086 A of the body 2082 A.
- the radially extending ribs 2064 A can include a recessed portions 2088 A ( FIG. 12 ) that receives a shoulder 2090 A ( FIG.
- the input load cam shroud 2020 A can be mounted on the input load cam 2005 A to, among other things, reduce the potential for the radially extending ribs 2064 A to generate unwanted fluid dynamics (for example, air and/or lubricant drag).
- FIGS. 17-19 show an alternative embodiment of an input load cam, which is referred to herein as the input load cam 3005 A.
- the input load cam 3005 A is suitably configured for being used in place of the input load cam 2005 A discussed above with reference to FIGS. 4 and 13 - 14 .
- the input load cam 3005 A includes a generally bowl-shaped body 3052 A having a hub portion 3054 A and a perimeter edge portion 3056 A.
- the body 3052 A has a conical shape.
- the hub portion 3054 A can include a central bore 3058 A having splines configured to mate with splines of the central portion 1010 of the main shaft 1000 ( FIG. 4 ), thereby facilitating power transfer from the main shaft 1000 to the variator 1200 .
- a set of bi-directional ramps 3060 A can be provided in a rear face 3062 A of the perimeter edge portion 3056 A.
- the ramps 3060 A can be configured for receiving the input load cam rollers 2015 A ( FIG. 7 ) and to cooperate with the input load cam rollers 2015 A for applying an axial force and a tangential force on the input traction ring 2010 A. Through such cooperation, the ramps 3060 A facilitate torque transfer from the input load cam 3005 A to the input traction ring 2010 A.
- Radial fins 3064 A can be attached to a front face 3066 A of the body 3052 A, extending outwardly from the perimeter edge portion 3056 A.
- the radial fins 3064 A serve, among other things, as cooling fins for dissipating heat. Furthermore, the radial fins 3064 A can be used for facilitating the sensing of the rotational speed of the input load cam 3005 A.
- the input load cam shroud 2020 A of FIGS. 10-12 is compatible with the input load cam 3005 A.
- the input load cam shroud 2020 A can be mounted on the input load cam 3005 A; however, in some embodiments, the input load cam shroud 2020 A is not used.
- a recess 3070 A in a front face 3071 A of the hub portion 3054 A can be configured for receiving an anti-rock device such as, for example, the anti-rock device 3072 A shown in FIG. 12 .
- a preloading spring recess 3076 A and a thrust bearing recess 3078 A are provided in a rear face 3079 A of the hub portion 3054 A.
- the preloading spring recess 3076 A is configured for receiving the preloading spring 2083 A ( FIG. 7 )
- the thrust bearing recess 3078 A is configured for receiving the thrust bearing 2085 A ( FIG. 7 ).
- such a preloading spring and thrust bearing arrangement serves to, among other things, exert a reactive preload force between the input load cam assembly 2000 A, the stator-manifold subassembly 2300 , and the output load cam assembly 2000 B.
- a plurality of dowel pin holes 3069 A ( FIGS. 18 and 19 ) in the front face 3071 A can be configured for receiving dowel pins (not shown) to facilitate coupling of the axial lock nut 1305 ( FIGS. 7 , 15 and 16 ) to the input load cam 3005 A for preventing unintentional loosening of the axial lock nut 1305 .
- the output load-cam-and-traction-ring subassembly 2000 B can include an output load cam 2005 B, an output traction ring 2010 B, a plurality of output load cam rollers 2015 B ( FIG. 20 ), an output load cam shroud 2020 B, an output load cam bearing assembly 2022 B, and a bearing support adapter 2024 B.
- the output load cam 2005 B can be mounted on the main shaft 1000 through use of the output load cam bearing assembly 2022 B and the bearing support adapter 2024 B.
- the output load cam bearing assembly 2022 B fits between the output load cam 2005 B and the bearing support adapter 2024 B.
- the output load cam bearing assembly 2022 B can be axially constrained by corresponding structural features of the output load cam 2005 B and the bearing support adapter 2024 B.
- the bearing support adapter 2024 B can include a central bore 2025 B configured for engaging a mating surface 1065 ( FIGS. 5 and 20 ) of the main shaft 1000 .
- the bearing support adapter can include a shoulder 2026 B configured to abut against the axial reaction flange 1020 of the main shaft 1000 to react axial loads that arise in the variator 1200 .
- the shoulder 2026 B is accessible through a first face 2016 B of the bearing support adapter 2024 B.
- the bearing adapter 2024 B can be mounted on the main shaft 1000 by, for example, an interference fit, press fit, or close tolerance clearance fit with the mating support surface 1065 of the main shaft 1000 .
- a flange 2027 B of the bearing support adapter 2024 B can be adapted to react axial loads from the output load cam bearing assembly 2022 B.
- the bearing support adapter 2024 B can include a piloting surface 2029 B that pilots on, or alternatively provides clearance with respect to, the axial reaction flange 1020 .
- the bearing support adapter 2024 B can include a recess 2077 B for receiving and supporting a spring 2087 B (see FIG. 20 ).
- the spring 2087 B can be a Bellville spring for providing preloading.
- a bearing support surface 2028 B of the bearing support adapter 2024 B can be configured to support the output load cam bearing assembly 2022 B.
- the bearing support adapter 2024 B can include a preloading spring recess 2076 B and a thrust bearing recess 2078 B, which are both accessible through a second face 2018 B of the bearing support adapter 2024 B.
- the preloading spring recess 2076 B is configured for receiving a preloading spring 2083 B ( FIG. 20 )
- the thrust bearing recess 2078 B is configured for receiving a thrust bearing 2085 B ( FIG. 20 ).
- such a preloading spring and thrust bearing arrangement serves to exert a reactive preload force between the input load cam assembly 2000 A, the stator-manifold subassembly 2300 , and the output load cam assembly 2000 B, when the preloading spring 2083 B is compressed.
- the preloading spring 2083 B include, but are not limited to, a Bellville washer, a wavy washer, a helical compression spring, and other suitably configured spring members.
- the thrust bearing 2085 B include, but are not limited to, a roller thrust bearing, a thrust bushing, and other devices suitably configured for carrying a thrust load.
- the thrust bearing recess 2078 B receives a bearing race adapted to cooperate with a needle bearing, which couples to a bearing race 4243 that is integral with, or positioned adjacent to, the stator 4200 (see FIG. 56 ).
- the output load cam 2005 B is coupled to the output traction ring 2010 B via the output load cam rollers 2015 B, which can be positioned between the output load cam 2005 B and the output traction ring 2010 B.
- the output traction ring 2010 B is placed between the output load cam rollers 2015 B and the planets 2102 . Torque exerted on the output traction ring 2010 B by the planets 2102 is transferred from the output traction ring 2010 B to the output load cam 2005 B through the load cam rollers 2015 B.
- the output load cam 2005 B can include a generally bowl-shaped body 2052 B having a hub portion 2054 B and a perimeter edge portion 2056 B.
- the hub portion 2054 B includes a central bore 2058 B having splines 2059 B configured to mate with splines of the second power input portion 1410 of the combining device 1400 ( FIG. 3A ), thereby facilitating power transfer from the variator 1200 to the combining device 1400 .
- the hub portion 2054 B can also include a bearing recess 2057 B configured for receiving an outer race of the output load cam bearing assembly 2022 B ( FIG. 20 ).
- a set of bi-directional ramps 2060 B is provided in a rear face 2062 B of the perimeter edge portion 2056 B.
- the ramps 2060 B can be configured for receiving the output load cam rollers 2015 B ( FIG. 20 ) and for cooperating with the output load cam rollers 2015 B for, among other things, applying an axial force on the output traction ring 2010 B.
- rotation of the output traction ring 2010 B causes the output load cam rollers 2015 B to urge the output traction ring 2010 B into compressive engagement with the planets 2102 and to urge the output load cam 2005 B into rotation about the longitudinal axis LA 1 of the main shaft 1000 , thereby providing for torque transfer from the planets 2102 to the output load cam 2005 B.
- Radially extending ribs 2064 B can be attached to a front face 2066 B of the body 2052 B, extending generally from the perimeter edge portion 2056 B to the hub portion 2054 B.
- the radially extending ribs 2064 B enhance stiffness of the body 2052 B and serve as cooling fins for dissipating heat, among other things.
- the radially extending ribs 2064 can be used for facilitating the sensing of rotational speed of the output load cam 2005 B.
- the output load cam 2005 B can include a hub portion 2054 B configured to engage the second power input portion 1405 of the combining device 1400 in a manner precluding relative rotation of the output load cam 2005 B with respect to the second power input portion 1405 . In this manner, the interface between the output load cam 2005 B and the second power input portion 1405 enables power transfer from the variator 1200 to the combining device 1400 .
- the output load cam shroud 2020 B can include a bowl-shaped body 2082 B having perimeter flanges 2084 B.
- the output load cam shroud 2020 B is mountable over the front face 2066 B of the output load cam 2005 B.
- each one of the perimeter flanges 2084 B is positioned between a respective adjacent pair of the radially extending ribs 2064 B, and the hub portion 2054 B of the output load cam 2005 B is exposed within a central opening 2086 B of the body 2082 B.
- the radially extending ribs 2064 B can include a recessed portions 2088 B ( FIG. 24 ) that receive shoulders 2090 B extending between adjacent ones of the perimeter flanges 2084 B.
- the shroud 2020 B can be mounted on the output load cam 2005 B to, among other things, reduce the potential for the radially extending ribs 2064 B to generate undesired fluid dynamics.
- FIGS. 27-29 show an alternative embodiment of an output load cam, which is referred to herein as the output load cam 3005 B.
- the output load cam 3005 B is suitably configured for being used in place of the output load cam 2005 B discussed above in reference to FIGS. 4 and 20 - 23 .
- the output load cam 3005 B includes a generally bowl-shaped body 3052 B having a hub portion 3054 B and a perimeter edge portion 3056 B.
- the hub portion 3054 B includes a central passage 3058 B having splines 3059 B configured to mate external splines of the second power input portion 1405 of the combining device 1400 , thereby facilitating power transfer from the variator 1200 to the combining device 1400 .
- the hub portion 3054 B can also include a bearing recess 3057 B configured for receiving an outer race of the output load cam bearing assembly 2022 B ( FIG. 20 ).
- a set of bi-directional ramps 3060 B can be provided in a rear face 3062 B of the perimeter edge portion 3056 B.
- the ramps 3060 B can be configured for receiving the output load cam rollers 2015 B ( FIG. 20 ) and to cooperate with the output load cam rollers 2015 B for applying an axial force on the output traction ring 2010 B and the output load cam 3005 B. Through such cooperation, the ramps 3060 B enable torque transfer from the output traction ring 2010 B to the output load cam 3005 B.
- radial fins 3064 B are attached to a front face 3066 B of the body 3052 B, extending outwardly from the perimeter edge portion 3056 B.
- the radial fins 3064 B serve as cooling fins for dissipating heat.
- the radial fins 3064 B can be used for facilitating the sensing of rotational speed of the output load cam 3005 B.
- the shroud 2020 B of FIG. 24 is compatible with the output load cam 3005 B.
- the shroud 2020 B can be mounted on the output load cam 3005 B to, among other things, reduce the potential for the radial fins 3064 B to generate undesirable fluid dynamics.
- each one of the planet-and-shift-lever subassemblies 2100 includes a planet 2102 rotatably mounted on a planet axle 2104 , which can be positioned on a planet central bore 2103 .
- Spaced apart planet bearings 2108 , an inner spacer 2110 , and outer spacers 2112 can mount coaxially on the planet axle 2104 .
- the inner spacer 2110 is positioned between the planet bearings 2108
- each one of the planet bearings 2108 is positioned between a respective one of the outer spacers 2112 and the inner spacer 2110 .
- each planet 2102 is rotatably mounted on a respective planet axle 2104 in a load-bearing and rotatable manner. It is disclosed herein that the present invention is not limited to a particular planet bearing and spacer arrangement for rotatably mounting each planet 2102 on the respective planet axle 2104 .
- a planet bearing and spacer arrangement using more than two or less two planet bearings and more than two or less spacers can be implemented.
- Planet axle shift levers 2106 (“shift levers 2106 ”) can be fixedly attached to opposing end portions 2107 of the planet axle 2104 such that the planet 2102 is positioned between the shift levers 2106 .
- the planet axle 2104 extends through a planet axle bore 2111 (see FIGS. 32 and 33 ) of each shift lever 2106 .
- the opposing end portions 2107 include a skew roller shoulders 2109 on which skew rollers 2122 mount.
- Each skew roller 2122 can be held in place by a washer 2124 and a clip ring 2126 , which clip ring 2126 can be engaged within a groove in the skew roller shoulder 2109 .
- a shift lever 2106 can include one or more features (not shown) such as, for example, a recess, a channel, etc., for providing clearance with other components of the variator 1200 .
- a shift guide roller axle 2116 can be engaged within a shift guide roller axle bore 2117 ( FIG. 33 ) of each shift lever 2106 and within a corresponding axle capturing feature 2119 ( FIGS. 32 and 33 ) of the planet axle 2104 .
- the shift guide roller axle bore 2117 intersects and is generally perpendicular to the planet axle bore 2111 .
- the shift guide roller axle bore 2117 is adjacent to a first end portion 2121 of the shift lever 2106 .
- the axle capturing feature 2119 include, but are not limited to, a feature generally characterized as a notch, a cut out, a channel, a seat, or the like.
- the shift guide roller axle 2116 and the corresponding axle capturing feature 2119 can be configured for limiting (for example, substantially precluding) radial displacement of the shift guide roller axle 2116 with respect to the engaged axle capturing feature 2119 .
- Such mating configuration of the shift guide roller axle 2116 and the corresponding axle capturing feature 2119 limits displacement of the shift lever 2106 along the longitudinal axis LA 2 of the planet axle 2104 when the shift guide roller axle 2116 is mounted on the planet axle 2104 with the shift guide roller axle 2116 engaged within the shift guide roller axle bore 2117 and the corresponding axle capturing feature 2119 ( FIGS. 32 and 33 ).
- Shift guide rollers 2114 can be mounted on opposing end portions of each shift guide roller axle 2116 .
- Each shift guide roller axle 2116 can be secured in place by, for example, washers 2118 and clip rings 2120 , which clip rings 2120 can be engaged within a groove 2191 of the shift guide roller axle 2116 .
- the shift guide roller axle 2116 can be secured by, for example, an interference fit, press fit, etc.
- a roller receiving channel 2129 is provided at a second end portion 2125 of each shift levers 2106 .
- a shift cam roller 2128 is positioned in the roller receiving channel 2129 .
- a shift cam roller axle 2130 extends through the shift cam roller 2128 and into engagement with axle receiving passages 2131 ( FIG. 33 ).
- the shift cam roller axle 2130 can be secured in place through an interference fit with the respective axle receiving passages 2131 .
- securing means such as a clip and groove arrangement can be implemented.
- the planet axle 2104 can have a through central bore 2134 and transverse channels 2142 in a substantially cylindrical body 2132 .
- the transverse channels 2142 enable fluid communication between the central bore 2134 and the space external of the planet axle 2104 , thereby allowing for lubrication of the bearings 2108 .
- the skew roller shoulders 2109 which are provided for receiving the skew rollers 2122 , are defined by a reduction in diameter of the cylindrical body 2132 .
- Grooves 2140 are provided in the skew roller shoulders 2109 for receiving the clip rings 2126 that constrain the skew rollers 2122 ( FIG. 32 ).
- the cylindrical body 2132 has a generally uniform diameter from over its entire length, such that reduction in diameter defining the skew roller shoulders 2109 is omitted and the skew rollers 2122 are corresponding configured for mating with uniform diameter of the cylindrical body 2132 .
- the shift-cam-and-sun subassembly 2200 can include sun 2202 , bearings 2204 , shift cams 2206 , control pistons 2208 , piston tube 2210 , shim 2212 , inner seals 2214 , and outer seals 2216 .
- the control pistons 2208 are coupled to the shift cams 2206 through the piston tube 2210 .
- the control pistons 2208 and the shift cams 2206 can be mounted on the piston tube 2210 by, for example, a press-fit interface.
- the sun 2202 can be operationally coupled to the shift cams 2206 through the bearings 2204 .
- the bearings 2204 can be configured to transfer axial and radial loads between the sun 2202 and the shift cams 2206 .
- the sun 2202 and the shift cams 2206 can be configured to receive the bearings 2204 .
- the inventive embodiments are not limited to bearings of a particular type.
- an angular contact bearing is a suitable bearing type for the bearings 2204 .
- the shim 2212 is positioned between the shift cams 2206 for setting a desired axial clearance between the sun 2202 and the shift cams 2206 .
- Such clearance facilitates relative rotation between the shift cams 2206 and the sun 2202 without allowing contact between adjacent surfaces.
- a plurality of shims can be used for achieving the desired clearance between the sun 2202 and the shift cams 2206 .
- the shim 2212 can be omitted and the shift cams 2206 and/or sun 2202 can be manufactured in a manner to achieve suitable clearance between the sun 2202 and the shift cams 2206 .
- the sun 2202 can have a body 2218 having a generally cylindrical outer diameter and internal recesses 2222 for receiving the bearings 2204 .
- the sun 2202 can have a central shoulder 2220 that facilitates axial constraint of the bearings 2204 , thereby limiting an insertion depth of each one of the bearings 2204 within the respective one of the recesses 2222 .
- the inventive embodiments are not limited to particular ways for positioning the bearings 2204 with respect to the body 2218 .
- a bearing 2204 has an outer race with an integral positioning flange that engages an exterior edge face 2223 of the sun 2202 .
- the recesses 2222 have a tapered face and each one of the bearings 2204 has an outer race with a tapered exterior surface that engages the tapered face of the respective one of the recesses 2222 .
- a discrete spacer can be used to facilitate proper spacing between the bearings 2204 .
- the outer races of the bearings 2204 can be formed integral with the sun 2202 , and/or the inner races of the bearing 2204 can be formed integral with the shift cam extensions 2206 .
- the shift cam 2206 can include a shift cam profile 2224 , which are adapted to guide the motion of the shift cam rollers 2128 .
- a shift cam profile 2224 which are adapted to guide the motion of the shift cam rollers 2128 .
- One embodiment of data points defining a shape of the shift cam profile 2224 is shown in the table of FIG. 41 .
- the X-dimension refers to an axial distance between a reference surface 2225 and the shift cam profile 2224 .
- the Y-dimension refers to a radial distance between a longitudinal centerline axis of a central bore 2228 of the shift cam 2206 and the shift cam profile 2224 .
- the shift cam 2206 includes a shift cam extension 2226 having an exterior face 2227 configured to receive a respective one of the bearings 2204 , and having an interior face 2229 configured to engage an exterior face 2252 of the piston tube 2210 .
- the shift cam extension 2226 includes a lubrication flow enhancing feature 2232 such as, for example a cut-out or notch.
- a rear face 2230 of the shift cam 2206 opposite to the shift cam profile 2224 is configured to be slightly angled relative to the reference surface 2225 for, among other things, promoting the flow of lubricant in the general area of the bearings 2204 and to maintain a desired clearance between the rear face 2230 of the shift cam 2206 and the exterior surfaces 2223 ( FIG. 39 ) of the sun 2202 .
- a control piston 2208 has a central bore 2249 configured for engaging an exterior face 2254 ( FIGS. 37 and 38 ) of the piston tube 2210 .
- the control piston 2208 has an internal recess 2250 and an external neck 2248 each configured for receiving and supporting the inner seal 2214 and the outer seal 2216 , respectively.
- the control piston 2208 has a piston face 2240 on which control fluid pressure exerts force.
- the control piston 2208 includes a number of recesses 2242 , wherein a recess 2242 can be configured to provide clearance for the second end portion 2125 ( FIG. 33 ) of a respective shift lever 2106 .
- Side faces 2244 of the recess 2242 can be configured to substantially constrain movement of the second end portion 2125 of the shift lever 2106 , thereby limiting rotation of the respective shift lever 2106 about the longitudinal axis LA 1 of the variator 1200 .
- the contoured shape of the recess 2242 can be used as a detectable proximity surface that facilitates the determination of a relative position of the control piston 2208 with respect to the longitudinal axis LA 1 .
- An anti-rotation feature 2246 (for example, a groove, pin, seat slot, etc.) can be provided in an exterior face of the control piston 2208 for engaging a mating anti rotation feature of an adjacent variator component to limit rotation of the control piston 2208 about the longitudinal axis LA 1 .
- the piston tube 2210 can include exterior faces 2252 , 2254 and a central bore 2256 .
- the faces 2252 can be configured to receive the shift cams 2206
- the faces 2254 can be configured to receive the control pistons 2208 .
- the outside diameter of the faces 2254 is nominally the same as each other, and the outside diameter of the faces 2252 are nominally the same as each other. In one embodiment, the outside diameter of the faces 2252 is slightly smaller than the outside diameter of the faces 2252 , which precludes having to press fit the shift cams 2206 over the respective outer engagement surface 2252 prior to press fitting it onto the respective inner engagement surface 2254 .
- the central bore 2256 can be configured to receive mating portions of a stator 4200 A, 4200 B (see FIG. 44 ) therein.
- the piston tube 2210 has a shim receiving recess 2260 (for example, a circumferential groove) for receiving a portion of the shim 2212 ( FIG. 38 ) and has an orifice 2259 for allowing passage of lubricant.
- the orifice 2259 is exposed within the shim receiving recess 2260 .
- the stator-manifold subassembly 2300 includes a center manifold 4000 , a first stator 4200 A, a second stator 4200 B, a first oil galley 4400 A and a second oil galley 4400 B.
- the first stator 4200 A attaches to a first side face 4005 of the center manifold 4000
- the second stator 4200 B attaches to a second side face 4010 of the center manifold 4000 .
- the first oil galley 4400 A mounts on the first stator 4200 A
- the second oil galley 4400 B mounts on the second stator 4200 B.
- the terms “oil”, “lubricant”, “lubricating fluid,” and “traction fluid” are generally interchangeable. Where appropriate, it will be clear by the context that the fluid, or condition, refers to lubrication rather than traction.
- the center manifold 4000 is configured for, among other things, facilitating the stator-manifold subassembly 2300 being fixedly mounted to the transmission housing 1800 of the transmission 600 ( FIG. 3A ), supporting the stators 4200 A, 4200 B, distributing control fluid and traction fluid to the variator 1200 ( FIGS. 3A and 44 ), and housing and supporting various sensors.
- sensors include, but are not limited to, sensors for sensing lubricant temperature, pressure, and viscosity.
- a sensor is provided for sensing the position of the shift lever subassembly 2100 relative to a surface on the stator 4200 .
- the stators 4200 A, 4200 B can be configured for, among other things, supporting the planet-and-shift-lever subassemblies 2100 , supporting the shift-cam-and-sun subassembly 2200 , and communicating control and traction fluids.
- the planet-and-shift-lever subassemblies 2100 are each movably supported jointly by the stators 4200 A, 4200 B and the shift-cam-and-sun subassembly 2200 .
- the shift-cam-and-sun subassembly 2200 cooperates with the stators 4200 A, 4200 B for facilitating control of movement of the planet-and-shift-lever subassemblies 2100 .
- the oil galleys 4400 A, 4400 B are configured for spraying (that is, delivering) lubricant onto portions of the planet-and-shift-lever subassemblies 2100 , the shift-cam-and-sun subassembly 2200 , and other components of the variator 1200 .
- the center manifold 4000 includes a base plate 4015 and a cover plate 4020 .
- the base plate 4015 includes a first side face 4016 A and a second side face 4016 B
- the cover plate 4020 includes a first side face 4021 A and a second side face 4021 B.
- the plates 4015 , 4020 are generally circularly shaped when viewed in a direction perpendicular to a respective side face.
- the plates 4015 , 4020 each has a cut-out pattern 4025 configured to generally surround the array of planet-and-shift-lever subassemblies 2100 ( FIG. 44 ).
- the plates 4015 , 4020 attach to each other in a side-by-side configuration as shown in FIGS. 44-48 with the cut-out pattern of the base plate 4015 being aligned with the cut-out pattern of the cover plate 4020 .
- the second side face 4016 B of the base plate 4015 abuts the first side face 4021 A of the cover plate 4020 when the plates 4015 , 4020 are placed in the side-by-side configuration.
- a first sensor cable groove 4027 and a second sensor cable groove 4029 can be provided in the first side face 4016 A of the base plate 4015 .
- Example sensors corresponding to such sensor cables include, but are not limited to, a gamma sensor, a fluid temperature sensor, and a speed measuring device sensor.
- the base plate 4015 includes bolt holes 4030 ( FIGS. 47 , 49 and 50 ), and the cover plate 4020 includes bolt holes 4031 ( FIGS. 48 , 52 and 53 ), which bolt holes 4030 , 4031 are configured to receive bolts (not shown) for securing the plates 4015 , 4020 in the side-by-side configuration.
- the bolt holes 4030 are counterbored, and the bolt holes 4031 include threads for having a threaded portion of the respective bolt engaged therewith.
- the bolt holes 4030 , 4031 can have different configurations that still provide for securing the plates 4015 , 4020 in the side-by-side configuration.
- the plates 4015 , 4020 preferably, but not necessarily, each include dowel pin holes 4035 .
- the dowel pin holes 4035 of the base plate 4015 and the dowel pin holes 4035 of the cover plate 4020 are located in the same relative positions with respect to the cut-out pattern 4025 .
- the dowel pin holes 4035 can be located radially in line with lubricant ports 4089 , 4087 of the respective plate 4015 , 4020 .
- engagement of dowel pins (not shown) within the dowel pin holes 4035 facilitates and simplifies proper alignment of the base plate 4015 with the cover plate 4020 .
- the base plate 4015 includes a footing 4040 (see FIGS. 45-46 and 49 - 50 ) configured for cooperating with the transmission housing 1800 ( FIG. 3A ) to provide torque reaction at the footing 4040 , thereby limiting movement of the base plate 4015 with respect to the transmission housing 1800 .
- Bolt holes 4043 receive bolts (not shown) for fastening the base plate 4015 to the transmission housing 1800 .
- the base plate 4015 includes locating pads 4045 that engage a mating structure (for example, a conformingly shaped recess, protruding ridge, etc.) of the transmission housing 1800 . The locating pads 4045 facilitate locating the base plate 4015 in the transmission housing 1800 .
- opposing ones of the locating pads 4045 include a cam wedge base 4050 that cooperates with a corresponding cam dowel 4055 (see FIGS. 45 and 51 A- 51 B) for fixedly engaging (for example, pressing) the base plate 4015 and/or the cover plate 4020 against one or more mating features of the transmission housing 1800 .
- the cam wedge base 4050 is a generally flat surface that is angled with respect to the first side face 4016 A of the base plate 4015 . Through such engagement, the center manifold 4000 can be positioned and, additionally, torque reaction can be provided adjacent one or more of the locating pads 4045 for limiting movement of the base plate 4015 with respect to the transmission housing 1800 .
- a cam dowel 4055 includes a generally cylindrical shaped cam body 4057 having a first end portion 4065 and a second end portion 4067 .
- the first end portion 4065 includes a cam wedge 4069 and the second end portion 4067 has a generally flat face 4070 (that is, extending generally perpendicular to a longitudinal reference axis of the cam body 4057 ).
- the cam wedge 4069 includes a face that is skewed with respect to the longitudinal reference axis of the cam body 4057 .
- the face of the cam wedge 4069 is generally flat.
- a threaded bore 4072 extends from the flat face 4070 at least partially toward the second end portion 4067 .
- the cam dowel 4055 resides within a threaded passage in a wall of the transmission housing 1800 , with the cam wedge 4069 extending from within the threaded passage into engagement with the cam wedge base 4050 .
- the cam dowel 4055 can be forced against the cam wedge base 4050 using, for example, a setscrew engaged within the threaded passage within the wall of the transmission housing 1800 .
- the threaded bore 4072 provides for engagement with a threaded extractor device for facilitating removal of the cam dowel 4055 from a passage of the transmission housing 1800 .
- the plates 4015 , 4020 are configured for routing lubricant and control fluid to the stators 4200 A, 4200 B. It is disclosed herein that the lubricant and the control fluid can be the same fluid used for different purposes (that is, lubricant and control). It is further disclosed herein that the lubricant and the control fluid can be the same as the transmission fluid discussed above in reference to FIG. 3A , which is advantageous in that it obviates the need to segregate such fluids.
- the base plate 4015 can include lubricant flow passages (not shown) that extend between a respective lubricant inlet port 4076 and a respective lubricant outlet port 4084 , thereby facilitating lubricant flow between corresponding lubricant inlet ports 4076 and lubricant outlet ports 4084 .
- the lubricant inlet ports 4076 receive lubricant from a lubrication fluid pump apparatus (not shown) of the transmission 600 or a standalone lubrication fluid pump apparatus.
- the base plate 4015 can include a first control fluid passage (not shown) that extends between a first control fluid inlet port 4078 and a first control fluid outlet port 4091 to allow flow of control fluid between the first control fluid inlet port 4078 and the first control fluid outlet port 4091 .
- the base plate 4015 can also include a second control flow passage (not shown) that extends between a second control fluid inlet port 4080 and a second control fluid outlet port 4092 to allow flow of control fluid between the second control fluid inlet port 4080 and the second control fluid outlet port 4092 .
- each lubricant inlet port 4076 , the first control fluid inlet port 4078 , and the second control fluid inlet port 4080 are located in a bottom edge face 4082 of the footing 4040 , as shown in FIG. 50 .
- the control fluid outlet ports 4091 , 4092 are in fluid communication with corresponding control fluid passages (not shown) that extend between the side faces 4016 A, 4016 B of the base plate 4015 .
- a first control fluid port 4093 of the cover plate 4020 FIGS.
- a second fluid control port 4094 of the cover plate 4020 aligns with the second control fluid outlet port 4092 of the base plate 4015 when the plates 4015 , 4020 are positioned in the side-by-side configuration.
- the center manifold 4000 can be configured so that lubricant flows from the lubricant inlet ports 4076 to the respective lubricant outlet ports 4084 and then into a lubricant distribution channel 4085 ( FIG. 52 ) in the first side face 4021 A of the cover plate 4020 .
- the lubricant distribution channel 4085 extends at least partially around a perimeter region of the cover plate 4020 .
- Branch lubricant channels 4086 extend between the lubricant distribution channel 4085 and lubricant ports 4087 and/or between the lubricant distribution channel 4085 and a respective lubricant spray port 4088 .
- the lubricant ports 4087 communicate with fluid passages (not shown) that extend between the side faces 4021 A, 4021 B of the cover plate 4020 .
- the lubricant ports 4087 align with lubricant ports 4089 when the plates 4015 , 4020 are positioned in the side-by-side configuration, thereby enabling the first stator 4200 A to receive lubricant from the lubricant ports 4089 , and the second stator 4200 B to receive lubricant from the lubricant ports 4087 .
- a spray of lubricant can be provided from the lubricant spray ports 4088 of the cover plate 4020 , which can be directed at, for example, the output traction interface TI 2 ( FIG. 44 ) between the output traction ring 2010 B and the planets 2102 (one shown in FIG. 44 ).
- the base plate 4015 can include lubricant spray ports 4090 (see FIG. 49 ) that each aligns with the lubricant distribution channel 4085 and/or a respective one of the branch lubricant channels 4086 , thereby facilitating the provision of a spray of lubricant from the lubricant spray ports 4090 , which can be directed at, for example, the input traction interface TI 1 ( FIG. 44 ) between the input traction ring 2010 A and the planets 2102 (one shown in FIG. 44 ).
- control fluid passages (not shown) extending between the control fluid inlet ports 4078 , 4080 and the respective control fluid outlet ports 4091 , 4092 allow independent and selective communication of control fluid with a control fluid pump apparatus (not shown) of the transmission 600 or stand alone apparatus. Through such independent and selective communication, a pressure differential between the control fluid passages can be produced. As discussed further below, selective control of this pressure differential facilitates selective adjustment of a position of the shift-cam-and-sun subassembly 2200 ( FIG. 44 ) with respect to the longitudinal axis LA 1 of the main shaft 1000 .
- the stators 4200 A, 4200 B are preferably, but not necessarily, essentially identical in construction and will both sometimes be referred to herein generically as the stator 4200 .
- the stator 4200 can include a number of shift lever guide flanges 4202 , a plurality of stator extensions 4204 , and a control piston receiver 4206 .
- the shift lever guide flanges 4202 attach to the control piston receiver 4206 in a radially extending and uniformly angularly spaced manner.
- a planet axle passage 4208 extends between each adjacent pair of shift lever guide flanges 4202 .
- the stator extensions 4204 extend axially from a first side face 4210 of each shift lever guide flange 4202 .
- the control piston receiver 4206 extends axially from a second side face 4212 of each shift lever guide flange 4202 .
- the shift lever guide flanges 4202 , the stator extensions 4204 , the control piston receiver 4206 A, and the planet axle passages 4208 are uniformly spaced and angularly arranged around a longitudinal axis LA 3 of the control piston receiver 4206 whereby the stator 4200 is generally circularly shaped and symmetrical with respect to the longitudinal axis LA 3 .
- a center manifold engagement face 4213 ( FIG. 55 ) of each one of the stator extensions 4204 is substantially flat and extends substantially perpendicular to the longitudinal axis LA 3 .
- the control piston receiver 4206 includes a receiver neck 4214 , a receiver end face 4216 , and a control piston engaging member 4218 .
- the control piston engaging member 4218 is generally a cylindrically shaped tubular body having an exterior surface 4222 and an interior surface 4224 .
- the interior surface 4224 defines a central bore 4225 of the control piston engaging member 4216 , which receives the main shaft 1000 .
- a circumferential seal groove 4227 (FIGS. 46 and 56 - 58 ) can be provided in the interior surface 4224 for receiving a seal (not shown) that engages a mating surface of the main shaft 1000 .
- a control piston receiving chamber 4220 is defined between the receiver neck 4214 , the receiver end face 4216 , and the control piston engaging member 4218 .
- the exterior surface 4222 of the control piston engaging member 4218 and an interior surface 4226 of the receiver neck 4214 extend substantially parallel to each other and serve as control piston support surfaces.
- the control piston receiving chamber 4220 is configured for receiving one of the control pistons 2208 ( FIG. 36-38 ).
- the exterior surface 4222 of the control piston engaging member 4218 is configured (for example, has a sufficient smoothness and straightness) for forming a sealed interface with the inner seal 2214 of the control piston 2208
- the interior surface 4226 of the receiver neck 4214 is configured for forming a sealed interface with the outer seal 2216 of the control piston 2208 .
- a longitudinal axis of the control piston engaging member 4218 extends coincidentally with the longitudinal axis LA 3 of the control piston receiver 4206 .
- the surfaces 4222 , 4226 are concentric about the longitudinal axis LA 3 .
- a skew roller reaction surface 4228 and a shift guide roller reaction surface 4230 are provided at opposing edges of each shift lever guide flange 4202 .
- the skew roller reaction surface 4228 is substantially flat and the shift guide roller reaction surface 4230 is contoured. Examples of such contour include, but are not limited to, semi-circular, parabolic, elliptical and angularly tapered. In one embodiment, the contour is circular and the center of its radius of curvature is coincident with the center of tilt of the planet 2102 .
- Adjacent skew roller reaction surfaces 4228 of adjacent shift lever guide flanges 4202 extend substantially parallel to each other and adjacent shift guide roller reaction surfaces 4230 of adjacent shift lever guide flanges 4202 are substantially aligned.
- a control fluid communicating bolt hole 4232 can be provided in one of the stator extensions 4204 .
- the control fluid communicating bolt hole 4232 can be configured to serve as a channel for fluid communication with the control piston receiving chamber 4220 .
- a lubricant communicating bolt hole 4234 can be provided in a number of other stator extensions 4204 .
- the lubricant communicating bolt hole 4234 can be configured to serve as a channel for providing lubricant to a planet/shift lever lubricant jet 4236 in the stator extension 4204 , to an oil galley feeding port 4238 in the receiver neck 4214 , and/or an output load cam assembly bearing lubricant jet 4240 in the receiver end face 4216 .
- the control fluid communicating bolt hole 4232 has a stepped profile such that a first portion of the control fluid communicating bolt hole 4232 , which is exposed at the second side face 4212 of the respective shift lever guide flange 4202 , has a relatively close clearance fit with the stator securing bolt and a second portion of the control fluid communicating bolt hole 4232 , which is exposed at the center manifold engagement face 4213 of the stator extension 4204 , has an oversize clearance fit with the stator securing bolt. In this manner, the flow of control fluid past the stator securing bolt in the second portion of the control fluid communicating bolt hole 4232 is essentially unrestricted.
- Drill holes 4242 that extend between the second portion of the control fluid communicating bolt hole 4232 and the control piston receiving chamber 4220 in an intersecting manner form a control fluid channel between the control fluid communicating bolt hole 4232 and the control piston receiving chamber 4220 .
- the openings of the drill holes 4242 exposed at the extension 4204 , exterior surface of the receiver neck 4214 , and at the exterior surface of the receiver end face 4216 are plugged to prevent control fluid discharge therefrom.
- a lubricant communicating bolt hole 4234 has a stepped profile such that a first portion of the lubricant communicating bolt hole 4234 , which is exposed at the second side face 4212 of the respective shift lever guide flange 4202 , has a relatively close clearance fit with the stator securing bolt and a second portion of the lubricant communicating bolt hole 4234 , which is exposed at the center manifold engagement face 4213 of the stator extension 4204 , has an oversize clearance fit with the stator securing bolt. In this manner, the lubricant flow past the stator securing bolt in the second portion of the lubricant communicating bolt hole 4234 is essentially unrestricted.
- the opening of the drill holes 4244 exposed at an exterior surface of the stator extensions 4204 can be plugged to prevent unintentional and/or undesirable lubricant discharge therefrom. For example, if the stator 4200 does not provide the output load cam bearing assembly 2022 B ( FIG. 20 ) with a dedicated supply of lubricant, the drill hole forming the output load cam assembly bearing lubricant jet 4240 is plugged.
- a drill hole 4246 ( FIGS. 55 , 57 and 59 ) extending through one of the shift lever guide flanges 4202 and the receiver neck 4214 forms a passage that can be used for routing wires and/or housing a sensor (not shown) such as, for example, a proximity sensor which cooperates with a contoured recess 2242 of the control piston 2208 for allowing a determination of the axial position of the control piston 2208 .
- the drill hole 4246 can be drilled from the outer diameter of the shift lever guide flange 4202 through the receiver neck 4214 into the control piston receiving chamber 4220 .
- a set screw hole 4248 can be formed in the receiver neck 4214 (for example, through one of the shift lever guide flanges 4202 ) for receiving an anti-rotation member (not shown) such as, for example, a set screw.
- the anti-rotation member cooperates with the groove 2246 ( FIG. 38 ) of a respective control piston 2208 for precluding rotation of the respective control piston 2208 within the control piston receiving chamber 4220 .
- the stator 4200 can include dowel pin holes 4250 for facilitating proper positioning of the stator 4200 with the center manifold 4000 .
- the dowel pin holes 4250 are located radially in line with the respective lubricant communicating bolt hole 4234 of the stator 4200 .
- the radial position of each dowel pin hole 4250 is substantially the same as the radial position of each dowel pin hole 4305 of the center manifold 4000 . Accordingly, dowel pins (not shown) of suitable length engaged with the dowel pin holes 4035 are coupled with corresponding dowel pin holes 4250 , thereby facilitating proper alignment of the stator 4200 with the center manifold 4000 .
- such a dowel pin hole arrangement enables positioning of the stator 4200 for aligning the control fluid communicating bolt hole 4232 of the stator 4200 with either one of the control fluid ports 4091 , 4092 of the base plate 4015 or with either one of the control fluid ports 4093 , 4094 of the cover plate 4020 , depending on which one of the plates 4015 , 4020 the stator 4200 is engaged with.
- the first stator 4200 A aligns with the first control fluid port 4091 of the base plate 4015
- the second stator 4200 B aligns with the second control fluid port 4093 of the cover plate 4020 , thereby allowing for communication of control fluid with the stators 4200 A, 4200 B.
- the first stator 4200 A engages the first side face 4005 of the center manifold 4000 ( FIGS. 45 and 46 ), and the second stator 4200 B engages the second side face 4010 of the center manifold 4000 . More specifically, the center manifold engagement face 4213 ( FIG. 55 ) of each stator extension 4204 of the first stator 4200 A engages the first side face 4016 A ( FIGS. 46 and 49 ) of the base plate 4015 , and the center manifold engagement face 4213 of each stator extension 4204 of the second stator 4200 B engages the second side face 4021 B ( FIGS. 48 and 53 ) of the cover plate 4020 .
- the first stator 4200 A is placed such that the control fluid communicating bolt hole 4232 ( FIGS. 54 and 55 ) of the first stator 4200 A aligns with the first control fluid passage 4091 ( FIG. 47 ) of the base plate 4015 and the lubricant distribution channel 4085 of the cover plate 4020 aligns with the lubricant port 4087 of the base plate 4015 .
- the second stator 4200 B can be placed such that control fluid communicating bolt hole 4232 ( FIGS. 53 and 54 ) of the second stator 4200 B aligns with the second control fluid port 4094 ( FIG. 47 ) of the cover plate 4020 and the lubricant communicating ports 4234 of the second stator 4200 B align with the lubricant ports 4087 of the cover plate 4020 .
- control fluid can be communicated to and from the control piston receiving chamber 4220 of the first stator 4200 A independently of control fluid communicated to and from the control piston receiving chamber 4220 of the second stator 4200 B, and lubricant can be delivered to various ports and jets of the stators 4200 A, 4200 B and oil galleys 4400 A, 4400 B independently of the control fluid.
- the oil galleys 4400 A, 4400 B are preferably, but not necessarily, essentially identical in construction and will both sometimes be referred to herein generically as the oil galley 4400 .
- the oil galley 4400 is generally circular and includes a central bore 4402 , an annular lubricant channel 4404 , a number of lubricant jet channels 4406 , and lubricant flow passages 4408 (for example, a drill hole).
- the lubricant jet ports 4406 can be arranged in groupings (for example, linear, cluster, etc.) that are preferably, but not necessarily, spaced (example, uniformly) around the central bore 4402 .
- Each group of lubricant jet ports 4406 can be in fluid communication with the annular lubricant channel 4404 by the respective lubricant flow passage 4408 .
- the oil galley 4400 includes stator bolt clearance cutouts 4410 configured to allow access to bolts engaged within the bolt holes 4232 , 4234 of the stators 4200 ( FIGS. 45 and 46 ) that secure the stators 4200 to the center manifold 2300 .
- the central bore 4402 can be configured to engage the exterior surface of the receiver neck 4214 ( FIGS. 45 and 46 ) of a respective stator 4200 by, for example, a press fit interface.
- the oil galley 4400 can be positioned on the receiver neck 4214 such that the annular lubricant channel 4404 aligns with the oil galley feeding port 4238 ( FIG. 56 ) of the stator 4200 , thereby facilitating supplying lubricant from the stator 4200 to the oil galley 4400 .
- the oil galley 4400 is angularly oriented such that each one of the groupings of the lubrication jet channels 4406 is aligned with a respective planet axle passage 4208 ( FIGS.
- the stators 4200 A, 4200 B and the center manifold 4000 are securely coupled in aligned orientation using a fastening structure such as, for example, a bolt and nut (not shown).
- a fastening structure such as, for example, a bolt and nut (not shown).
- an elongated portion of a threaded fastening structure extends through the bolt holes 4232 , 4234 of the stators 4200 A, 4200 B and the lubricant ports 4087 , 4089 of the center manifold plates 4015 , 4020 .
- the threaded fastening structure is tightened such that end portions of the threaded fastening structure (for example, the head of the bolt) apply a compressive force on the stators 4200 and the center manifold 4000 to form a substantially rigid support structure for components and subassemblies to be mounted thereon.
- sealing washers are used under the bolt head and nut to seal the lubrication and control fluid passages.
- a first control piston 2208 A ( FIG. 63 ) of the shift-cam-and-sun subassembly 2200 is slidably mounted within the control piston receiving chamber 4220 (see FIGS. 56 and 57 ) of the first stator 4200 A
- a second control piston 2208 B ( FIG. 63 ) of the shift-cam-and-sun subassembly 2200 is slidably mounted within the control piston receiving chamber 4220 the second stator 4200 B.
- the shift-cam-and-sun subassembly 2200 can be selectively and controllably displaced along the longitudinal axis LA 1 of the main shaft 1000 .
- the control pistons 2208 A, 2208 B are constrained from rotation about the longitudinal axis LA 1 .
- each planet 2102 (one shown in FIG. 63 ) with the input traction ring 2010 A, the output traction ring 2010 B, and the sun 2202 constrains axially and radially the planet 2102 of each planet-and-shift-lever subassembly 2100 .
- the planet 2102 is rotatably mounted on the respective planet axle 2104 .
- the skew roller 2122 ( FIG. 63 )
- a planet-and-shift-lever subassembly 2100 engages skew roller reaction surfaces 4228 of adjacent shift lever guide flanges 4202 positioned within a respective planet axle passage 4208 , thereby substantially precluding rotation of the respective planet-and-shift-lever subassembly 2100 about any radial axis extending perpendicular to the longitudinal axis LA 1 .
- the two shift guide rollers 2114 of each shift lever 2106 engage respective shift guide roller reaction surfaces 4230 .
- a first one of the shift guide rollers 2114 engages a shift guide roller reaction surface 4230 on a first side of the respective planet axle passage 4208
- a second one of the shift guide rollers 2114 engages a shift guide roller reaction surface 4230 on a second side of the respective planet axle passage 4208
- the semi-circular shape of the shift guide roller reaction surfaces 4230 and the corresponding engagement by the shift guide rollers 2114 serves to, among other things, substantially preclude axial displacement of the respective planet-and-shift-lever subassemblies 2100 with respect to relative to the longitudinal axis LA 1 , as well as to reduce the force needed to effect a tilting of the planet axles 2104 .
- shift guide roller reaction surfaces 4230 cooperate with the shift guide rollers 2114 to react the shift forces that arise by the actuation of the planet-and-shift-lever subassemblies 2100 by the shift-cam-and-sun subassembly 2200 .
- each planet-and-shift-lever subassembly 2100 is substantially axially and radially constrained relative to the longitudinal axis LA 1 , and constrained with respect to rotation about any radial axis extending perpendicular to the longitudinal axis LA 1 .
- each planet-and-shift-lever subassembly 2100 is pivotable about the respective tangential reference axis TA 1 , which extends through a center point of the respective planet 2102 substantially perpendicular to a radial reference axis extending from the longitudinal axis LA 1 through the center point of the respective planet 2102 .
- the planet 2102 is configured to freely move axially along the axis LA 2 to allow for dimensional tolerances stack up between the traction components and the shift reaction surfaces. Additionally, the center of rotation of the planet axle 2104 is not necessarily coincident with the center of rotation of the planet 2102 ; such configuration prevents, in some cases, efficiency losses, increased shift forces, or outright binding of the variator 1200 .
- the shift cam roller 2128 of each shift lever 2106 couples to a cam surface of a respective shift cam 2206 .
- a differential control fluid pressure between the control piston receiving chambers 4220 causes an axial translation of the shift-cam-and-sun subassembly 2200 along the axis LA 1 .
- Such axial translation results in force being exerted on the shift cam rollers 2128 coupled to the shift cam 2206 facing the direction of movement, thereby causing the planet-and-shift-lever subassemblies 2100 to synchronously pivot about the respective tangential reference axis TA 1 .
- control fluid pressure within the control piston receiving chambers 4220 serves to hold the shift-cam-and-sun subassembly 2200 in a given position due to equal and opposing reactive forces being applied by the shift cams 2206 on the respective shift cam roller 2128 .
- adjustment of the speed ratio of the variator 1200 is facilitated through axial translation of the shift-cam-and-sun subassembly 2200 along the longitudinal axis LA 1 .
- the bell housing 1810 includes a prime mover mounting portion 1812 and a rear housing mounting portion 1814 .
- the prime mover mounting portion 1812 can be configured for attachment to a structural portion of the prime mover (for example, a engine block, motor casing, etc.), and the rear housing mounting portion 1814 can be configured for attachment to the rear housing 1820 of the transmission housing 1800 ( FIG. 3A ).
- the torque converter subassembly 800 is an embodiment of an input interface, which is suitably configured for implementation between a prime mover (not shown) and the variator 1200 .
- the torque converter subassembly 800 can include a flex plate assembly 802 , a torque converter 804 ( FIGS. 66 and 67 ), and a transmission fluid pump 806 ( FIGS. 66 and 67 ).
- the flex plate assembly 802 includes a flex plate 803 and starter gear ring 807 for enabling a rotary apparatus (for example, a starter motor) to turn moving components of the prime mover such as for starting the prime mover.
- the flex plate 803 is configured for attachment to a power output portion (for example, a crankshaft or motor shaft) of the prime mover in a manner that precludes relative rotation of the flex plate 803 with respect to the power output portion of the prime mover, thereby enabling torque transfer from the prime mover to the flex plate 803 .
- the flex plate 803 typically connects to the prime mover with threaded fasteners (such as bolts).
- the torque converter 804 includes a converter torque output portion 805 ( FIG. 66 ), a torque converter housing 808 , and various torque converting components (not shown) within the torque converter housing 808 that enable torque converter fluid within the torque converter housing 808 to be conveyed within the housing 808 in a manner that transfers torque applied to the torque converter housing 808 to the torque converter output portion 805 .
- the torque converter output portion 805 includes a turbine and a splined hub that fixedly attach to the turbine. The splined hub mates with the splines of the first end portion 1005 ( FIGS. 3A , 4 and 5 ) of the main shaft 1000 .
- the torque converter housing 808 is configured for attachment to the flex plate 803 in a manner that substantially precludes relative rotation of the torque converter housing 808 with respect to the flex plate 803 , thereby facilitating torque transfer from the flex plate 803 to the torque converter housing 808 .
- Examples of such ways for attaching the torque converter housing 808 to the flex plate 803 include, but are not limited to, threaded fastener structures, pins, and the like.
- the transmission fluid pump 806 includes a pump housing 812 , a torque input shaft 814 , and various fluid pumping components within the pump housing that facilitate application of torque to the torque input shaft 814 to cause transmission fluid to be drawn into the pump housing 812 via a fluid supply input (not shown) and supplied from within the pump housing 812 under pressure via a fluid outlet (not shown).
- the pump housing 812 fixedly attaches to a pump mounting structure 815 of the bell housing 1820 .
- the torque input shaft 814 attaches to the torque converter housing 808 in a manner that substantially precludes relative rotation of the torque input shaft 814 with respect to the torque converter housing 808 , thereby facilitating torque transfer from the torque converter housing 808 to the torque input shaft 814 .
- the combining device 1400 can be an output interface, which is suitably configured for implementation between the main shaft 1000 , the variator 1200 , and the rangebox 1600 . More specifically, the main shaft 1000 and the variator 1200 supply power to the first power input portion 1405 and the second power input portion 1410 , respectively, of the combining device 1400 , and the power output portion 1422 of the combining device 1400 supplies power to the rangebox 1600 .
- the combining device 1400 can include a hub 1416 , a plurality of planet gears 1418 , a plurality of planet gear axles 1419 , a planet gear carrier 1420 , a power output portion (or a transfer shaft) 1422 , a needle bearing 1424 , a forward disk 1426 , a rear disk 1428 , a sun gear 1430 , and a thrust ring 1432 .
- the planet gears 1418 are each rotatably mounted on the planet gear carrier 1420 via one of the planet gear axles 1419 ( FIG. 71 ).
- Each planet gear 1418 is positioned within a pocket region of the planet gear carrier 1420 and the respective planet gear axle 1419 is engaged within respective planet gear axle bores 1421 of the planet gear carrier 1420 .
- the sun gear 1430 is positioned within the pocket region of the planet gear carrier 1420 , and the teeth of the sun gear 1430 are configured to engage the teeth of the planet gears 1418 .
- the sun gear 1430 includes a central bore having internal splines 1431 , which are configured to engage splines at the second end portion 1015 of the main shaft 1000 .
- the transfer shaft 1422 includes splines 1434 , 1436 , 1438 , and 1440 .
- the splines 1434 engage mating splines of an extension portion 1442 of the planet gear carrier 1420 .
- the needle bearing 1424 is mounted within a pocket of the transfer shaft 1422 . As shown in FIG. 3A , a tip of the main shaft 1000 engages the needle bearing 1424 , thereby providing an aligned and supported interface therebetween.
- the splines 1436 , 1438 , and 1440 are engaged with mating components of the rangebox 1600 .
- the rear disk 1428 can be configured to engage teeth adjacent a rear edge 1444 of the hub 1416 , thereby precluding relative rotation of the rear disk 1428 with respect to the hub 1416 .
- the planet gear carrier 1420 is positioned within the hub 1416 with a rear face of the planet gear carrier 1420 abutting the rear disk 1428 .
- the teeth of the planet gears 1418 engage mating interior teeth of the hub 1416 .
- the second power input portion 1410 of the combining device 1400 includes the hub 1416 .
- the thrust ring 1432 is positioned within the hub 1416 , abutting a front face of the planet gear carrier 1420 .
- the forward disk 1426 engages internal splines formed on a front edge 1446 of the hub 1416 , thereby precluding relative rotation of the forward disk 1426 with respect to the hub 1416 .
- the forward disk 1426 and the rear disk 1428 axially constrain the planet gear carrier 1420 , reacting axial thrust in either direction from the sun gear 1430 .
- a first circumferential groove 1448 and a second circumferential groove 1450 are provided adjacent the front edge 1446 and the rear edge 1444 , respectively, and are each configured for respectively receiving a retention device such as, for example, a respective snap ring engaged therein for axially constraining the disks 1426 , 1428 . Still referring to FIGS.
- exterior splines 1435 can be provided at the front edge 1446 of the hub 1416 .
- the exterior splines 1435 are configured for coupling to splines of the output load cam 2005 B, for example.
- the combining device 1400 is configured for facilitating power transfer from the variator 1200 to the coupling device 1400 .
- the main shaft 1000 can be coupled directly to the input load-cam-and-traction-ring subassembly 2000 A and to a first power input portion 1405 of the combining device 1400 .
- Each of the planets 2102 (one shown) is engaged between the input load-cam-and-traction-ring subassembly 2000 A, the output load-cam-and-traction-ring subassembly 2000 B, and the sun 2202 .
- the input load cam 2005 A couples to the input traction ring 2010 A through the input load cam rollers 2015 A.
- the output load cam 2005 B couples to the output traction ring 2010 B through the output load cam rollers 2015 B.
- the output load cam 2005 B couples to the second power input portion 1410 of the combining device 1400 .
- the transfer shaft 1422 of the combining device 1400 couples to a direct clutch 1604 and to a sun gear 1606 of a first planetary gearset 1608 of the rangebox 1600 .
- the first planetary gearset 1608 is supported on a carrier 1609 .
- a sun gear 1610 of a second planetary gearset 1612 is configured for being selectively coupled to the transfer shaft 1422 through the direct clutch 1604 or to the transmission housing 1800 .
- the sun gear 1610 couples to the transmission housing 1800 through either a forward clutch 1614 , via an overrun clutch 1616 (for example, a one-way mechanical diode), or a low clutch 1618 .
- the sun gear 1610 couples to the first planetary gearset 1608 .
- a ring gear 1622 couples to the first and second planetary gearsets 1608 , 1612 and to a reverse clutch 1624 of the rangebox 1600 .
- An output shaft 1626 couples to the carrier 1609 .
- the output shaft 1626 and the carrier 1609 are one integral part.
- the rangebox 1600 is provided in a vehicle having an engine supplying power to the transmission 600 .
- the rangebox 1600 is controlled in conjunction with the variator 1200 for providing the transmission 600 with multiple modes of operation, in which the shifting control of the variator 1200 is based on engine speed, vehicle speed, and/or user commands.
- a first power train operating mode (for example, Mode 1 ) refers to the rangebox 1600 being engaged in a low gear range.
- a second power train operating mode (for example, Mode 2 ) refers to the rangebox 1600 being engaged in a high gear range with the variator 1200 in overdrive (that is, speed output from the range box is greater than speed input to the range box).
- the variator 1200 is maintained in an underdrive condition until the engine reaches a predetermined engine speed set point such as, for example, 1800 revolutions-per-minute (rpm). Once the predetermined engine speed set point is achieved, the engine speed is held constant while the variator 1200 shifts its torque ratio in a manner that causes the vehicle speed to increase. Vehicle speed continues to increase until the variator 1200 reaches a torque ratio corresponding to maximum overdrive, at which point, the engine speed increases up to a predetermined maximum engine speed (for example, maximum recommended engine rpm, peak horsepower, etc.).
- a predetermined engine speed set point such as, for example, 1800 revolutions-per-minute (rpm).
- the rangebox 1600 is shifted from Mode 1 to Mode 2 , with the variator 1200 in overdrive.
- the engine speed is initially decreased to cause synchronization between vehicle speed and engine speed.
- the engine can then be controlled to increase speed further by increasing engine speed with the variator in overdrive.
- one or more data processing units are programmed for facilitating the operating modes discussed above.
- a power train controller, an engine controller, and/or a transmission controller are examples of data processing units, which can be programmed for providing the operating modes discussed above.
- Various sensors and control devices are connected to the engine and/or transmission 600 for facilitating the implementation of such modes of operation.
- a hydraulic control structure having valving can be used to convert electronic control algorithms to hydraulic and mechanical actuation of the variator 1200 and/or rangebox 1600 .
- the rangebox 1600 can include an intermediate support 1640 , a high and low mode subassembly 1642 , and a reverse mode subassembly 1644 .
- FIGS. 75-77 Various aspects of the rear housing 1820 of the transmission housing 1800 discussed above in reference to FIGS. 3A and 3B are shown in FIGS. 75-77 .
- a bell housing attachment portion 1816 of the rear housing 1820 is configured for attachment to the rear housing mounting portion 1814 of the bell housing 1810 .
- a tail housing attachment portion 1818 of the rear housing 1820 is configured for attachment with a tail housing (not shown) of the transmission 600 or to a housing of a related drivetrain subassembly.
- the rear housing 1820 includes an access port 1822 configured for receiving and supporting a sensor (not shown) for monitoring speed of the input load cam 2005 A.
- An access port 1824 is configured for receiving and supporting a sensor for monitoring speed of the output load cam 2005 B.
- Passages 1826 are configured for receiving and supporting the cam dowels 4055 discussed above in reference to FIGS. 45-51 .
- each passage 1826 is at least partially threaded for receiving a threaded fastener (for example, a setscrew) used for exerting a retention force on the respective cam dowel 4055 .
- a support flange 1828 is provided within an interior space of the rear housing 1820 for locating and axially supporting the center manifold 4000 through engagement with the locating pads 4045 discussed above in reference to FIGS. 45-51 .
- a center manifold footing engagement shoulder 1830 is provided for engaging the footing 4040 of the center manifold 4000 .
- Threaded holes 1831 are provided in the center manifold footing engagement shoulder 1830 for attaching the footing 4040 to the center manifold footing engagement shoulder 1830 .
- a locating diameter 1832 is provided within the interior space of the rear housing 1820 .
- a series of clutch splines 1834 and grooves 1836 are formed in interior wall surfaces of the rear housing 1800 and are configured for receiving and supporting various components and/or assemblies of the rangebox 1600 (for example, clutches, gears, gearsets, snap rings, etc.).
- various ports are provided in a bottom wall 1838 of the rear housing 1820 .
- Lubricant ports 1842 can be configured for communicating lubricant to the lubricant inlet ports 4076 of the base plate 4015 of the center manifold 4000 ( FIG. 50 ).
- First and second control fluid ports 1844 , 1846 are provided for facilitating selective and independent communication of control fluid with, respectively, the first and second control fluid inlet ports 4078 , 4080 of the base plate 4015 ( FIG. 50 ).
- a group of ancillary ports 1848 can be provided for facilitating selective and independent communication of other desired fluids with transmission components such as, for example, an external fluid cooler, an external fluid pump, etc., and/or for facilitating the mounting of one or more sensors (for example, a lubricant temperature sensor, a lubricant level sensor, etc.).
- transmission components such as, for example, an external fluid cooler, an external fluid pump, etc.
- sensors for example, a lubricant temperature sensor, a lubricant level sensor, etc.
Abstract
Description
- This application claims the benefit of, and herby incorporates by reference herein in its entirety, U.S. Provisional Application 60/889,512, filed on Feb. 14, 2007.
- 1. Field of the Invention
- The disclosed invention relates generally to mechanical power modulation and transmission. More specifically, the invention concerns continuously variable units and transmissions, subassemblies, components, and methods for use therewith.
- 2. Description of the Related Art
- In the relevant technology various types of continuously variable transmissions (CVT) are known. The particular type of CVT which pertains to the present disclosure is typically known as a ball-type rolling traction CVT. Although ball-type rolling traction CVTs have gained some acceptance in certain industrial applications, the technology has generally been unable to overcome technical and economic hurdles to gain a wider adoption across multiple fields of use.
- The inventive embodiments disclosed here address many of the challenges that have prevented ball-type rolling traction CVTs from gaining wider acceptance in the marketplace. In particular, though certainly not limited in scope of applicability, the inventive embodiments disclosed here provide mechanisms and methods for employing ball-type continuously variable units and/or continuously variable transmissions in automotive applications.
- The systems and methods herein described have several features, no single one of which is solely responsible for its desirable attributes. Without limiting the scope as expressed by the claims that follow, its more prominent features will now be discussed briefly. After considering this discussion, and particularly after reading the section entitled “Detailed Description of Certain Inventive Embodiments” one will understand how the features of the system and methods provide several advantages over traditional systems and methods.
- One aspect of the invention relates to a drive having a prime mover and a transmission coupled to the prime mover. In one embodiment the transmission has a continuously variable unit (CVU), an input interface coupled to the prime mover and to the CVU, and an output interface coupled to the CVU. The drive also has a parallel branch for mechanical power transmission. The parallel branch can be coupled to the input interface and to the output interface.
- Another aspect of the invention addresses a transmission having a main shaft, an input load cam, an input traction ring, and a first set of load cam rollers positioned between the input load cam and the input traction ring. In one embodiment, the transmission has a number of traction planets in contact with the input traction ring, and the transmission has a traction sun in contact with the traction planets. In some embodiments, the transmission has an output traction ring in contact with the traction planets, an output load cam, and a second number of load cam rollers positioned between the output traction ring and the output load cam. In one embodiment, the transmission has a planetary gearset that has a sun gear, a ring gear, and a carrier. The output load cam is coupled to the ring gear, and the main shaft is coupled to the sun gear. The transmission can also have a transfer shaft coupled to the planetary gear set carrier.
- One more aspect of the invention concerns a transmission including a number of traction rollers, a carrier assembly operably coupled to the traction rollers, and an input element configured to transfer torque to the traction rollers. The input element includes a load cam and a traction ring that each has bidirectional load cam ramps. In one embodiment, the transmission includes an output element configured to transfer torque from the traction rollers. The transmission also includes a shifter assembly configured to adjust an axis of rotation of the traction rollers. In some embodiments, the transmission includes a hydraulic system operably coupled to the shifter assembly, and the transmission includes a lubrication system configured to provide lubricant to at least the traction rollers.
- Yet another aspect of the invention involves a drive having a torque converter, a main shaft coupled to the torque converter, an input load cam coupled to the main shaft, and an input traction ring operationally coupled to the input load cam. The drive also includes a number of traction planets adapted to receive torque from the input traction ring. In one embodiment, the drive includes an output traction ring adapted to receive torque from the traction planets and an output load cam operationally coupled to the output traction ring. The drive also includes a planetary gearset coupled to the output load cam and to the main shaft.
- One aspect of the invention concerns a transmission having a number of spherical traction rollers, a carrier assembly for supporting the traction rollers, an input element for transferring torque to the traction rollers, and an output element for transferring torque from the traction rollers. In one embodiment, the transmission includes an axial force generator for applying a clamping force to the spherical rollers, input element, and output element. The transmission includes a shifter assembly for adjusting an axis of rotation of the spherical traction rollers. In one embodiment, the transmission includes a hydraulic system for actuating the shifter assembly, and the transmission includes a lubrication system for providing lubricant to at least the spherical traction rollers.
- Another aspect of the invention relates to a continuously variable unit (CVU) having a rotatable main shaft, an input load cam coupled to the main shaft, an input traction ring operationally coupled to the input load cam, and a number of traction planets in contact with the input traction ring. In one embodiment, the CVU includes an output traction ring in contact with the traction planets and an output load cam operationally coupled to the output traction ring. The CVU also includes a traction sun in contact with the traction planets. A number of planet axles define the axes of rotation for the traction planets. The CVU includes at least one shift lever for each planet axle. The CVU also includes at least one shift cam operationally coupled to the shift levers and at least one stator configured to axially and radially support the planet axles and the shift levers. The CVU includes at least one control piston configured to actuate an axial movement of the at least one shift cam, and the CVU can include a center manifold configured to support the at least one stator. The center manifold is also configured to provide control fluid and lubricant to the CVU.
- Yet one more aspect of the invention addresses a continuously variable unit (CVU) having a number of traction planets arranged angularly about a longitudinal axis of the CVU. The CVU includes a traction sun in contact with the traction planets and a number of planet axles coupled to the traction planets. The planet axles define the axes of rotation for the traction planets. The CVU includes a number of shift levers. At least one shift lever is coupled to each planet axle. The CVU includes a shift cam operably coupled to the shift levers, and the CVU has a stator configured to axially and radially support the planet axles and the shift levers. The CVU also includes at least one control piston configured to actuate an axial movement of the shift cam and a center manifold configured to support the stator. The center manifold is adapted to provide a control fluid and a lubricant to the CVU.
- In another aspect, the invention concerns a continuously variable unit (CVU) having an input element configured to receive a power input, a number of traction members coupled to the input element, a carrier assembly adapted to facilitate support of the traction members, and a load-cam-and-traction-ring subassembly configured to generate axial force. The CVU includes a shifter assembly operably coupled to the traction members and an output element configured to receive power from the traction members. In one embodiment, the CVU includes a hydraulic system configured to be in fluid communication with the shifter assembly.
- Another aspect of the invention relates to a shifting mechanism for a rolling traction transmission. The shifting mechanism includes a traction sun, a number of shift cams, and a number of control pistons operationally coupled to the shift cams. In one embodiment, the traction sun is placed between the shift cams.
- One aspect of the invention relates to a control piston for a shifting mechanism of a continuously variable unit (CVU). The control piston includes a generally cylindrical body having a central bore adapted to engage a piston tube. In one embodiment, the control piston includes a piston face configured to interface with control fluid and a surface configured to facilitate sensing of an axial position of the control piston. Another aspect of the invention relates to a control piston a control piston tube having a generally cylindrical tube with a through central bore. The control piston tube includes a surface adapted to couple to a control piston, and the control piston tube has a surface adapted to coupled to a shift cam.
- Another aspect of the invention addresses a shift cam for a shifting mechanism of a continuously variable unit (CVU). The shift cam includes a central bore, a shift cam profile, and a shift cam extension. In some embodiments, the shift cam profile is substantially defined by the data points shown in
FIG. 41 . In other embodiments, the shift cam has an angled face adapted to allow lubricant flow. In yet other embodiments, the central bore of the shift cam is adapted to couple to a control piston tube. - One more aspect of the invention concerns a piston tube for use in a rolling traction transmission. The piston tube includes a substantially annular cylindrical body having a center bore, a first face located on the outer circumference of the annular cylindrical body, and a second face located on the outer circumference of the annular cylindrical body. The first face is configured to receive a shift cam of the transmission. The second face is configured to receive a control piston of the transmission. The piston tube also includes an orifice located on the outer circumference of the annular cylindrical body. The orifice is adapted to provide a lubricant to the transmission.
- Yet another aspect of the invention involves a stator-manifold assembly having a center manifold and at least one stator coupled to the center manifold so that the center manifold provides, and the stator receives, control fluid and lubricant. In some embodiments, the stator-manifold assembly includes at least one oil galley in fluid communication with the at least one stator.
- One aspect of the invention concerns a center manifold for a continuously variable unit (CVU). The center manifold includes a base plate having a number of channels and ports for receiving and distributing control fluid and lubricant. In one embodiment, the center manifold includes a cover plate adapted to couple to the base plate. The cover plate has a number of channels and ports for receiving and distributing control fluid and lubricant.
- Another aspect of the invention relates to a base plate for a center manifold of a continuously variable unit (CVU). The base plate includes a number of ports and channels for receiving and distributing fluid, and a number of recesses for clearing one or more traction planets of the CVU. In one embodiment, the base plate includes one or more structures for facilitating the locating and fastening of the base plate to a housing of the CVU. The base plate also includes a number of channels for receiving and housing sensor cables.
- Yet one more aspect of the invention addresses a stator for a continuously variable unit (CVU). The stator includes a number of extensions adapted to facilitate the coupling of the stator to a manifold. The extensions comprise one or more channels for receiving and distributing fluid. The stator includes a tubular body configured to form a chamber for receiving a control fluid and a control piston. The stator also includes an extension configured to deliver lubricant to an oil galley.
- In another aspect, the invention concerns a cover plate for continuously variable unit (CVU). The cover plate includes a substantially circular shaped body. The circular shaped body has a first side face, a second side face, and a cut-out pattern configured to substantially surround an array of planet-and-shift-lever subassemblies of the CVU. The cover plate includes a number of lubricant channels arranged on the first side face. The cover plate also includes a number of lubricant spray ports positioned to be in fluid communication with the lubricant channels.
- Another aspect of the invention relates to an oil galley for a continuously variable unit (CVU). The oil galley includes a central bore having an annular recess for receiving fluid. In one embodiment, the oil galley has a number of radial channels extending substantially radially from the annular recess toward an outer perimeter of the oil galley. The radial channels are spaced angularly about the central bore. The oil galley also includes a number of axial channels that extend substantially axially from each of the radial channels.
- One aspect of the invention relates to a transmission housing having one or more structures for retaining and locating a center manifold. The transmission housing includes a number of ports for delivering and receiving fluids to internal components of the transmission. In one embodiment, the transmission housing includes a number of ports for receiving a number of sensors. The transmission housing also includes one or more passages for receiving one or more cam dowels configured to cooperate with structures of the transmission housing and/or the center manifold for retaining and locating the center manifold.
- Another aspect of the invention addresses a main shaft for a continuously variable transmission (CVT). The main shaft includes an elongated body having a first end portion, a central portion, and a second end portion. The main shaft includes a set of torque converter engagement splines formed on the first end portion. A first engagement extension extends from the torque converter engagement splines. The main shaft includes a set of combining device engagement splines formed on the second end portion. A second engagement extension extends from the second end portion. In one embodiment, the main shaft includes an axial reaction flange located on the second end portion.
- One more aspect of the invention concerns a main shaft for a continuously variable transmission (CVT). The main shaft includes an elongated body having a first end portion, a central portion, and a second end portion. In one embodiment, the main shaft includes a number of input load cam engagement splines formed on the central portion and an axial reaction flange located on the second end portion.
- Yet another aspect of the invention involves a traction ring for use in a continuously variable transmission. The traction ring includes a substantially annular ring having a front face and a back face. In one embodiment, the traction ring includes a contact surface formed on the front face. The traction also includes a groove formed on the back face.
- One aspect of the invention concerns a load cam for use in a continuously variable transmission (CVT). The load cam includes a bowl shaped body having a perimeter edge portion and a hub portion. The hub portion has a central bore. The load cam includes a cylindrically shaped flange that is concentric with the hub portion. In one embodiment, the load cam includes a number of ribs radially extending from the hub portion to the perimeter edge portion. The ribs intersect the flange. The load cam also includes a number of bi-directional ramps formed on a face of the perimeter edge portion.
- Another aspect of the invention relates to an input load cam shroud for use in a continuously variable transmission. The input load cam shroud includes a bowl shaped body having a central opening. In one embodiment, the input load cam includes several flanges formed about the perimeter of the bowl shaped body. The flanges form a number of shoulders that are adapted to engage a number of mating features of a load cam of the CVT.
- Yet one more aspect of the invention addresses an input load cam assembly for use in a continuously variable transmission. The input load cam assembly includes a load cam and a load cam shroud. The load cam has a bowl shaped body with a perimeter edge portion and a hub portion having a central bore. The load cam includes a cylindrically shaped flange concentric with the hub portion and a number of ribs extending from the hub portion to the perimeter edge portion. The ribs intersect the flange. The load cam also includes a number of bi-directional ramps formed on a face of the perimeter edge portion. The load cam shroud includes a bowl shaped body having a central opening. The load cam shroud also includes a number of flanges formed about the perimeter of the bowl shaped body. The flanges form a plurality of shoulders adapted to engage a plurality of mating features of a load cam shroud of the CVT.
- In another aspect, the invention concerns a load cam for use in a continuously variable transmission. The load cam includes a substantially bowl shaped body having a hub portion and a perimeter edge portion. The perimeter edge portion has a front face and a rear face. The load cam includes a number of fins arranged angularly around the front face of the perimeter edge portion. The load cam also includes a number of bi-directional ramps formed on a rear face of the perimeter edge portion.
- Another aspect of the invention relates to an axial lock nut for use in a continuously variable transmission (CVT). The axial lock nut includes a substantially cylindrical body that has a threaded central bore, an extension portion, and a polygon-shaped outer periphery portion. A number of notches are formed on the outer periphery portion. The notches are configured to couple to a dowel pin of the CVT. The axial lock nut also includes an anti-rock piloting surface formed on the central bore.
- One aspect of the invention relates to a bearing support adapter for use in a continuously variable transmission (CVT). The bearing support adapter includes a substantially cylindrical body having a first face, a second face, and a central bore. In one embodiment, the bearing support adapter has a flange extending radially from the first face. The flange is configured to react axial force. The bearing support adapter also includes a bearing support surface located on the outer circumference of the cylindrical body and a shoulder arranged on the central bore in proximity to the first face. In one embodiment, the bearing support adapter has a thrust bearing recess formed on the second face.
- Another aspect of the invention addresses a continuously variable transmission having a main shaft, a number of spherical planets, a first load-cam-and-traction-ring subassembly, a second load-cam-and-traction-ring subassembly, and a bearing support adapter. The main shaft is arranged along a longitudinal axis of the transmission and adapted to receive a power input. The planets are arranged angularly about the longitudinal axis of the transmission. The first load-cam-and-traction-ring subassembly is operably coupled to the main shaft and to the spherical planets. The second load-cam-and-traction-ring subassembly is operably coupled to the spherical planets. The bearing support adapter is coupled to the main shaft and configured to support a bearing coupled to the second load-cam-and-traction-ring subassembly.
- One more aspect of the invention concerns a shift-cam-and-sun subassembly for a continuously variable transmission (CVT). The shift-cam-and-sun subassembly includes a traction sun, a shift cam operably coupled to the traction sun, and a piston tube coupled to the shift cam. The piston tube is coaxial with the traction sun. The shift-cam-and-sun subassembly also includes a control piston coupled to the piston tube. The control piston is coaxial with the traction sun.
- Yet another aspect of the invention involves a traction sun for a continuously variable transmission (CVT). The traction sun includes a generally cylindrical body having a central bore. A first recess is formed on the central bore, and is configured to receive a bearing. A central shoulder is formed on the central bore, and is in proximity to the first recess. The traction sun also includes an exterior edge face formed on the outer circumference of the cylindrical body. The exterior edge face configured to be a rolling contact surface for number of traction planets of the CVT.
- One aspect of the invention concerns a shift cam for a continuously variable transmission (CVT). The shift cam includes a substantially disc-shaped body having a front face, a rear face, and a central bore. In one embodiment, the shift cam has an extension surface extending from the central bore. The shift cam has a reference surface formed on the rear face. The shift cam also has a shift cam profile formed on the front face. A set of coordinates define the shape of the shift cam profile. The coordinates are based on the reference surface and include those of the data table shown in
FIG. 41 . - Another aspect of the invention relates to a cam dowel having a substantially cylindrical body with a central bore, a first end portion, and a second end portion. The cam dowel includes a cam wedge formed on the first end portion. The cam dowel also includes a substantially flat face formed on the second end portion.
- Yet one more aspect of the invention addresses a combining device for a continuously variable transmission (CVT). The combining device includes a transfer shaft, a hub, a number of planet gears, a planet gear carrier, and a sun gear. The transfer shaft is an elongated body with a first end, a second end, and a central bore. The hub is operably coupled to the transfer shaft and is coaxial with the transfer shaft. The planet gears are operably coupled to the hub. The planet gear carrier is configured to support the planet gears. In one embodiment of the combining device, the sun gear is coupled to the planet gears. The sun gear has a central bore configured to couple to a main axle of the CVT.
- In another aspect, the invention concerns a combining device for use in a continuously variable transmission (CVT). The combining device includes a hub configured to support a planetary gear set. In one embodiment, the combining device has a first power input portion operably coupled to the hub. The hub has a second power input portion. The combining device also has a power output portion operably coupled to the hub.
- Another aspect of the invention relates to a continuously variable transmission having a rotatable main shaft arranged along the longitudinal axis of the transmission. In one embodiment, the transmission includes a variator having a number of traction planets arranged angularly about the longitudinal axis of the transmission. The transmission includes a combining device operably coupled to the variator and to the main shaft. The transmission also includes a rangebox operably coupled to the combining device.
- One aspect of the invention relates to a rangebox for use in a continuously variable transmission (CVT). The rangebox includes a power input portion configured to receive power from a transfer shaft of the CVT, and an output shaft arranged along the longitudinal axis of the rangebox. The output shaft is configured to transfer power out of the rangebox. The rangebox includes a high-and-low mode subassembly configured to receive power from the power input portion. The high-and-low mode subassembly is arranged along the longitudinal axis of the range box and coaxial with the output shaft. The rangebox includes a reverse mode subassembly configured to receive power from the power input portion. The reverse mode subassembly is operably coupled to the output shaft. The rangebox also includes an overrun clutch operably coupled to the high-and-low mode subassembly and arranged between the forward clutch and the power input portion.
- Another aspect of the invention addresses a planet axle for supporting rotation of a traction roller and facilitating a tilting of the axis of rotation. The planet axle includes a generally cylindrical body having a through bore along a longitudinal axis of the cylindrical body. In one embodiment, the planet axle also includes one or more axle capturing features for engagement of a transverse axle.
- One more aspect of the invention concerns a shift lever for a continuously variable transmission (CVT). The shift lever has an elongated body with a first end portion and a second end portion. The shift lever includes a first bore formed on the first end portion. The first bore is configured to receive a planet axle of the CVT. In one embodiment, the shift lever has a second bore formed on the first end portion. The second bore intersects the first bore in a substantially perpendicular location. The second bore is configured to receive a shift guide roller axle of the CVT. The shift lever also has an axle receiving passage formed on the second end. The axle receiving passage is configured to receive a shift cam roller axle of the CVT.
- Yet another aspect of the invention involves a planet-and-shift-lever mechanism for use in a continuously variable transmission. The planet-and-shift-lever mechanism includes a spherical planet having a central bore, a planet axle placed in the central bore, and a first shift lever coupled to a first end of the planet axle. In one embodiment, the planet-and-shift-lever mechanism has a second shift lever coupled to a second end of the planet axle and a first skew roller coupled to the first end of the planet axle. The planet-and-shift-lever mechanism also has a second skew roller coupled to the second end of the planet axle, a first shift cam roller coupled to the first shift lever, and a second shift cam roller coupled to the second shift lever.
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FIG. 1 is a high-level block diagram showing an embodiment of adrive apparatus 100 that includes an inventive continuously variable transmission and continuously variable unit. -
FIG. 2 is a schematic diagram of one embodiment of continuously variable transmission and continuously variable unit in accordance with certain inventive teachings of the disclosure. -
FIG. 3A is a cross-sectional view of one embodiment of a continuously variable transmission employing a continuously variable unit. -
FIG. 3B is a partially exploded view of the continuously variable transmission ofFIG. 3A . -
FIG. 4 is a partial cross-section of certain components of a continuously variable unit (CVU). -
FIG. 5 is a perspective view of a shaft that can be used with the CVU ofFIG. 4 . -
FIG. 6 is a cross-sectional view of the shaft ofFIG. 5 . -
FIG. 7 is a partial cross-section of certain components of the CVU ofFIG. 4 . -
FIG. 8 is a perspective view of a traction ring that can be used with the CVU ofFIG. 4 . -
FIG. 9 is a cross-sectional view of the traction ring ofFIG. 8 . -
FIG. 10 is a perspective view of a load cam and shroud assembly that can be used with the CVU ofFIG. 4 . -
FIG. 11 is a perspective view of the load cam and shroud assembly ofFIG. 10 . -
FIG. 12 is a partially exploded view of the load cam and shroud assembly ofFIG. 10 . -
FIG. 13 is a perspective view of a load cam that can be used with the CVU ofFIG. 4 . -
FIG. 14 is a cross-sectional view of the load cam ofFIG. 13 . -
FIG. 15 is a perspective view of a lock nut that can be used with the CVU ofFIG. 4 . -
FIG. 16 is a cross-sectional view of the lock nut ofFIG. 15 . -
FIG. 17 is a perspective view of yet another load cam that can be used with the CVU ofFIG. 4 . -
FIG. 18 is yet another perspective of the load cam ofFIG. 17 . -
FIG. 19 is a cross-sectional view of the load cam ofFIG. 17 . -
FIG. 20 is a partial cross-section of certain components of the CVU ofFIG. 4 . -
FIG. 21 is a perspective view of yet another load cam that can be used with the CVU ofFIG. 4 . -
FIG. 22 is a cross-sectional view of the load cam ofFIG. 21 . -
FIG. 23 is another perspective view of the load cam ofFIG. 21 . -
FIG. 24 is a perspective view of a shroud that can be used with the CVU ofFIG. 4 . -
FIG. 25 is a perspective view of a bearing support adapter that can be used with the CVU ofFIG. 4 . -
FIG. 26 is a cross-sectional view of the bearing support adapter ofFIG. 25 . -
FIG. 27 is a perspective view of yet another load cam that can be used with the CVU ofFIG. 4 . -
FIG. 28 is another perspective view of the load cam ofFIG. 27 . -
FIG. 29 is a cross-sectional view of the load cam ofFIG. 27 . -
FIG. 30 is a partial cross-sectional view of certain components of the CVU ofFIG. 4 . -
FIG. 31 is a perspective view of a planet-and-shift-lever subassembly that can be used with the CVU ofFIG. 4 . -
FIG. 32 is a cross-sectional view of certain components of the planet-and-shift-lever subassembly ofFIG. 31 . -
FIG. 33 is an exploded view of the planet-and-shift-lever-subassembly ofFIG. 32 . -
FIG. 34 is a perspective view of a planet axle that can be used with the CVU ofFIG. 4 . -
FIG. 35 is a cross-sectional view of the planet axle ofFIG. 34 . -
FIG. 36 is a perspective view of a shift-cam-and-sun subassembly that can be used with the CVU ofFIG. 4 . -
FIG. 37 is a cross-sectional view of certain components of the shift-cam-and-sun subassembly ofFIG. 36 . -
FIG. 38 is an explode view of certain components of the shift-cam-and-sun subassembly ofFIG. 37 . -
FIG. 39 is a cross-sectional view of a sun that can be used with the CVU ofFIG. 4 . -
FIG. 40 is a cross-sectional view of a shift cam that can be used with the CVU ofFIG. 4 . -
FIG. 40A is a detail view A of the shift cam ofFIG. 40 . -
FIG. 41 is a data table with data points specifying a suitable profile for the shift cam ofFIG. 40 . -
FIG. 42 is a cross-sectional view of a control piston that can be used with the CVU ofFIG. 4 . -
FIG. 43 is a perspective view of a piston tube that can be used with the CVU ofFIG. 4 . -
FIG. 44 is a partial, cross-sectional view of certain components of the CVU ofFIG. 4 . -
FIG. 45 is a perspective view of a stator-manifold subassembly that can be used with the CVU ofFIG. 4 . -
FIG. 46 is a cross-sectional view of certain components of the stator-manifold ofFIG. 45 . -
FIG. 47 is a perspective view of a center manifold that can be used with the stator-manifold ofFIG. 45 . -
FIG. 48 is a second perspective view of the center manifold ofFIG. 47 . -
FIG. 49 is a perspective view of a base plate that can be used with the center manifold ofFIG. 47 . -
FIG. 50 is a second perspective view of the base plate ofFIG. 49 . -
FIG. 51A andFIG. 51B are perspective views of a cam dowel that can be used with the CVU ofFIG. 4 and the stator-manifold subassembly ofFIG. 45 . -
FIG. 52 is a plan view of a cover plate that can be used with the center manifold ofFIG. 47 . -
FIG. 53 is a perspective view of the cover plate ofFIG. 52 . -
FIG. 54 is a perspective view of a stator that can be used with the CVU ofFIG. 4 . -
FIG. 55 is a second perspective view of the stator ofFIG. 54 . -
FIG. 56 is a cross-sectional view of the stator ofFIG. 54 . -
FIG. 57 is yet another cross-sectional view of the stator ofFIG. 54 . -
FIG. 58 is yet another cross-sectional view of the stator ofFIG. 54 . -
FIG. 59 is side view of the stator ofFIG. 54 . -
FIG. 60 is a perspective view of an oil galley that can be used with the CVU ofFIG. 4 . -
FIG. 61 is a second perspective view of the oil galley ofFIG. 60 . -
FIG. 62 is a cross-sectional view of the oil galley ofFIG. 60 . -
FIG. 63 is a partial, cross-sectional view of certain components of the CVU ofFIG. 4 . -
FIG. 64 is a yet another cross-sectional view of certain components of the CVU ofFIG. 4 . -
FIG. 65 is a perspective view of a bell housing and certain components of an input interface that can be used with transmissions ofFIGS. 1 , 2, and 3A. -
FIG. 66 is a cross-sectional, partial perspective view of the bell housing ofFIG. 65 . -
FIG. 67 is a partially explode view of certain components of the bell housing and input interface ofFIG. 65 . -
FIG. 68 is a perspective view of a combining device that can be use with the transmission oFIG. 3A . -
FIG. 69 is a side view of the combining device ofFIG. 68 . -
FIG. 70 is a cross-sectional view of the combining device ofFIG. 68 . -
FIG. 71 is a partially exploded view of certain components of the combining device ofFIG. 67 . -
FIG. 72 is a schematic diagram of a continuously variable unit adapted to cooperate with a rangebox. -
FIG. 73 is a perspective view of one embodiment of a range box that can be used with the CVU ofFIG. 4 and/or the transmission ofFIG. 3A . -
FIG. 74 is a cross-sectional view of the rangebox ofFIG. 73 . -
FIG. 75 is a perspective view of a rear housing that can be used with the transmission ofFIG. 3A . -
FIG. 76 is a cross-sectional, perspective view of certain components and features of the rear housing ofFIG. 75 . -
FIG. 77 is a plan view of the bottom side of the rear housing ofFIG. 75 . - Certain inventive embodiments will now be described with reference to the accompanying figures, wherein like numerals refer to like elements throughout. The terminology used in the description presented herein is not intended to be interpreted in any limited or restrictive manner simply because it is being utilized in conjunction with a detailed description of certain specific embodiments of the invention. Furthermore, embodiments of the invention may include several novel features, no single one of which is solely responsible for its desirable attributes or which is essential to practicing the inventions herein described. The CVT/IVT embodiments described here are generally related to transmissions and variators disclosed in U.S. Patent Application 60/890,438, the entire disclosure of which is hereby incorporated herein by reference.
- As used here, the terms “operationally connected,” “operationally coupled”, “operationally linked”, “operably connected”, “operably coupled”, “operably linked,” and like terms, refer to a relationship (mechanical, linkage, coupling, etc.) between elements whereby operation of one element results in a corresponding, following, or simultaneous operation or actuation of a second element. It is noted that in using said terms to describe inventive embodiments, specific structures or mechanisms that link or couple the elements are typically described. However, unless otherwise specifically stated, when one of said terms is used, the term indicates that the actual linkage or coupling may take a variety of forms, which in certain instances will be obvious to a person of ordinary skill in the relevant technology.
- For description purposes, the term “radial” is used here to indicate a direction or position that is perpendicular relative to a longitudinal axis of a transmission or variator. The term “axial” as used here refers to a direction or position along an axis that is parallel to a main or longitudinal axis of a transmission or variator. For clarity and conciseness, at times similar components labeled similarly (for example, control piston 582A and control piston 582B) will be referred to collectively by a single label (for example, control pistons 582).
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FIG. 1 is a high-level block diagram showing an embodiment of adrive apparatus 100, which is referred to herein as thedrive 100. In some embodiments, thedrive 100 includes atransmission 101 operationally coupled between aprime mover 102 and aload 114. Theprime mover 102 delivers power to thetransmission 101, and thetransmission 101 delivers power to theload 114. Theprime mover 102 can be one or more of any number of power generating devices, and theload 114 can be one or more of any number of driven devices or components. Examples of theprime mover 102 include, but are not limited to, engines, motors and the like. Examples of loads include, but are not limited to, drivetrain differential assemblies, power take-off assemblies, generator assemblies, pump assemblies, and the like. - In one embodiment, the
transmission 101 includes aninput interface 104, avariator 106, a parallel branch 108 (for example, a fixed ratio branch), anoutput interface 110, and arangebox 112. Theinput interface 104 is operationally coupled to theprime mover 102. Thevariator 106 and theparallel branch 108 can be operationally coupled in parallel between theinput interface 104 and theoutput interface 110. Therangebox 112 is operationally coupled between theoutput interface 110 and theload 114. - The
input interface 104 can be configured for receiving power from theprime mover 102 and transferring such power to thevariator 106 and theparallel branch 108 in a distributed manner. Theoutput interface 110 can be configured for combining power (that is, torque applied at a given rotational speed) from thevariator 106 and theparallel branch 108 and transferring such combined power to therangebox 112. It is disclosed herein that neither theinput interface 104 nor theoutput interface 110 is necessarily limited to a particular respective physical and/or operational configuration. Accordingly, theinput interface 104 may include any gearing or coupling structure suitable for providing such distributed power transfer and distribution functionality, and theoutput interface 110 may include any gearing or coupling structure suitable for providing such combined power transfer functionality. Examples of theinput interface 104 include, but are not limited to, a torque converter assembly, a hydraulic clutch coupling, a manually actuated clutch assembly, a computer-controlled clutch assembly, a magnetorheological clutch coupling, and the like. - The
parallel branch 108 can be configured for enabling power distributed thereto from theinput interface 104 to be directly transferred to theoutput interface 110 without any selective variation (that is, adjustment) of rotational speed and/or rotational direction associated with that power. However, in other embodiments, theparallel branch 108 can be configured to modulate power in discrete (that is, stepped) or continuously variable modes. Thevariator 106 can be configured for enabling power distributed thereto from theinput interface 104 to be transferred to theoutput interface 110 in a manner whereby torque and/or rotational speed associated with that power is selectively variable (that is, selectively adjustable). Accordingly, a torque split unit in accordance with one embodiment of the present invention comprises thevariator 106 and theparallel branch 108 and provides for two power paths between theinput interface 104 and theoutput interface 110. A first one of the power paths extends through thevariator 106 and a second one of the power paths extends through theparallel branch 108. As will be discussed below in greater detail, power distribution between the two power paths is dependent upon a selectively variable ratio of an input power specification of the variator 106 (for example, input torque and input rotational shaft speed) with respect to an output power specification of the variator 106 (for example, output torque and output rotational shaft speed). One reason for implementing a split torque unit is to increase a torque capacity of thetransmission 101. For example, during a duty cycle that requires a high torque output, it is desirable to route a majority of such high torque through theparallel branch 108 thereby precluding torque carrying components of the variator 106 from having to experience long periods of high torque application. Preferably, but not necessarily, a transmission in accordance with the present invention is of a split torque type. However, it is disclosed herein that theparallel branch 108 may, in some embodiment of the present invention, be omitted such that power is transferred between theinput interface 104 and theoutput interface 110 solely through thevariator 106. - The
rangebox 112 provides various gear selection and clutch engagement functionalities. Examples of such gear selection functionality include, but are not limited to, selective engagement of available rangebox gear ratios and selective engagement of various load drive directions. Examples of such clutch engagement functionality include, but are not limited to, passive implementation of various clutch engagement operations and active implementation of various clutch engagement operations. - Referring to
FIG. 2 now, one embodiment of thetransmission 101 will be described. As shown inFIGS. 1 and 2 , theinput interface 104 can serve as a torque interface for receiving an applied input torque at a given rotational speed or range of rotational speeds from theprime mover 102. Through theinput interface 104, the applied input torque is delivered to thevariator 106 and theparallel branch 108 in a distributed manner. Torque is distributed dependent upon a torque ratio setting of thevariator 1200. - As discussed above, the
parallel branch 108 can be configured to receive power from theinput interface 104 and to distribute that power directly to theoutput interface 110 without any selective variation of rotational speed and/or rotational direction associated with that power. In one embodiment, theparallel branch 108 includes a shaft rotatably coupled between theinput interface 104 and theoutput interface 110 for transferring power from theinput interface 104 and theoutput interface 110 without any selective variation of rotational speed and/or rotational direction associated with that power. - As shown in
FIG. 2 , in one embodiment thevariator 106 can includetraction members 202, aninput element 204, ashifter assembly 206, an axial force generator (AFG) 208, acarrier assembly 210, ahydraulic system 212, alubrication system 214, and anoutput element 216. Theinput element 204, theshifter assembly 206, theaxial force generator 208, thecarrier assembly 210, thelubrication system 214, and theoutput element 216 are operationally coupled to thetraction members 202. Thehydraulic system 212 is operationally connected to theshifter assembly 206 and is configured for adjusting a torque ratio setting of thevariator 106. Theinput element 204 is operationally coupled to theinput interface 104 for receiving power from theinput interface 104. Power is transmitted frominput element 204 to theoutput element 216 through thetraction members 202. Power is output from thevariator 106 through theoutput element 216, being delivered to theoutput interface 110. - The
carrier assembly 210 provides for physical placement and support of thetraction members 202. Theshifter assembly 206 provides functionality for selectively manipulating thetraction members 202, thereby enabling a ratio of input torque exerted on theinput element 204 to output torque exerted on the output element 216 (that is, the torque ratio) to be selectively varied in a continuous, or stepless, manner. In doing so, theshifter assembly 206 enables the amount of torque transferred jointly by thevariator 106 and theparallel branch 108 between theinput interface 104 and theoutput interface 110 to be selectively varied. Thehydraulic system 212 can be configured for hydraulically controlling theshifter assembly 206 to vary the torque ratio. Thelubrication system 214 can be configured to deliver a lubricant to, among other things, mechanical interfaces betweentraction members 202, theinput element 204, and theoutput element 216. In one embodiment, thelubrication system 214 is adapted to provide lubricant to therangebox 112. Theaxial force generator 208 can be configured for exerting a force (for example, clamping force, axial force, etc.) to keep theinput element 204 and theoutput element 216 in sufficient contact with thetraction members 202, thereby limiting slippage at points of contact therebetween. In some embodiments, theaxial force generator 208 can cooperate with, or be at least partly operationally coupled with thehydraulic system 212. - Still referring to
FIG. 2 , in one embodiment, therangebox 112 includes afirst rangebox structure 220 configured for varying a gear range, asecond rangebox structure 222 configured for adjusting a load drive direction, and athird rangebox structure 224 configured to protect against load overrun conditions. Thefirst rangebox structure 220 preferably facilitates selective adjustment between a rangebox high gear ratio (for example, relatively low torque output exerted at a relatively high rotational speed) and a rangebox low gear ratio (for example, relatively high torque output exerted at a relatively low rotational speed), which increases the overall gear ratio range of thetransmission 101. Thesecond rangebox structure 222 can be configured to facilitate selective adjustment between a first rotary drive direction (for example, corresponding to driving theload 114 in a forward operational direction) and a second rotary drive direction (for example, corresponding to driving theload 114 in a reverse operational direction). Thethird rangebox structure 224 is adapted to facilitate mechanical slippage in the case where theload 114 attempts to back drive theprime mover 102 through thetransmission 101. - Passing to
FIGS. 3A and 3B now, various aspects of atransmission 600 will now be discussed. In one embodiment, thetransmission 600 can include atorque converter subassembly 800, amain shaft 1000, avariator 1200, a combiningdevice 1400, arangebox 1600, and atransmission housing 1800. Thetransmission housing 1800 can include a bell housing 1810 (that is, a first housing portion) and a rear housing 1820 (that is, a second housing portion) separably connected to thebell housing 1810. In the embodiment illustrated, thetorque converter subassembly 800, themain shaft 1000, thevariator 1200, the combiningdevice 1400, and therangebox 1600 are operably mounted on or within thetransmission housing 1800 in an axially aligned manner. Thus, it is disclosed herein that thetransmission housing 1800 is configured for housing and supporting various subassemblies and/or components of thetransmission 600. In other embodiments, any one of thetorque converter subassembly 800, thevariator 1200, the combiningdevice 1400, and therangebox 1600 can be arranged in a parallel shaft configuration relative to the other components. - In some embodiments, the
variator 1200 and themain shaft 1000 can be operably coupled between a power output portion of thetorque converter subassembly 800 and power input portions of the combiningdevice 1400. In operation, thetorque converter subassembly 800 transfers power to thevariator 1200 through themain shaft 1000. Thevariator 1200 supplies power to a firstpower input portion 1410 of the combiningdevice 1400. Themain shaft 1000 supplies power to a secondpower input portion 1405 of the combiningdevice 1400. Power from thevariator 1200 and themain shaft 1000 can be supplied to the combiningdevice 1400 in a selectively variable ratio (for example, power from thevariator 1200 in relation to power from the main shaft 1000) and can be combined by the combiningdevice 1400. The combiningdevice 1400 delivers the combined power to therangebox 1600 via apower output portion 1401 of the combiningdevice 1400. Thepower output portion 1401 can include a carrier of planetary gear set and/or a transfer shaft. - In one embodiment, the
variator 1200 mounts on themain shaft 1000. In one configuration, thevariator 1200 and themain shaft 1000 form a torque split unit. More specifically, the ratio of torque transferred to the combiningdevice 1400 through thevariator 1200 or through themain shaft 1000 is selectively variable dependent upon a torque ratio setting of thevariator 1200. To this end, thevariator 1200 transfers power to the combiningdevice 1400 in a manner whereby the torque and/or the rotational speed associated with that power is selectively and continuously variable (that is, adjustable). Thus, thevariator 1200 can be configured for receiving power of a first specification (for example, first torque and first rotational shaft speed) and outputting power of a second specification (for example, second torque and second rotational shaft speed). - The
torque converter subassembly 800 is one embodiment of aninput interface 104, for example, thereby providing the functionality of transferring power from a prime mover attached to thetorque converter subassembly 800 to thevariator 1200 via, for example, themain shaft 1000. In other embodiments, a different type of input interface such as, for example, a manually controlled clutch subassembly, a computer controlled clutch assembly, or a flywheel can be implemented in place of thetorque converter subassembly 800. The combiningdevice 1400 is an embodiment of an output interface, thereby providing the functionality of combining power received from thevariator 1200 and themain shaft 1000 and transferring such power to therangebox 1600. In one embodiment, therangebox 1600 receives power from the combiningdevice 1400 and outputs power in conjunction with providing one or more of the various gear selection and clutch engagement functionalities discussed above in reference toFIGS. 1 and 2 . As is discussed further below, therangebox 1600 in combination with thevariator 1200 enables thetransmission 600 to operate in multiple modes (that is, a multi-mode transmission). - Referring to
FIGS. 3A and 4 , in one embodiment, thevariator 1200 can include an input load-cam-and-traction-ring subassembly 2000A, an output load-cam-and-traction-ring subassembly 2000B, an array of planet-and-shift-lever subassemblies 2100, a shift-cam-and-sun subassembly 2200, and a stator-manifold subassembly 2300. In one embodiment, the shift-cam-and-sun subassembly 2200 is supported by the stator-manifold subassembly 2300. The shift-cam-and-sun subassembly 2200 is supported in a manner enabling the shift-cam-and-sun subassembly 2200 to be translated along a longitudinal axis LA1 of themain shaft 1000. The planet-and-shift-lever subassemblies 2100 are arrayed angularly around themain shaft 1000, and are supported jointly by the shift-cam-and-sun subassembly 2200 and the stator-manifold subassembly 2300. Each one of the planet-and-shift-lever subassemblies 2100 is supported in a manner that facilitates synchronous rotation of all the planet-and-shift-lever subassemblies 2100 about a respective reference axis TA1 extending through aplanet 2102 of each one of the planet-and-shift-lever subassemblies 2100. Through such synchronous rotation, all of the planet-and-shift-lever subassemblies 2100 are in the same relative rotational position at a given point in time. The axis TA1 (seeFIG. 4 ) associated with each one of the planet-and-shift-lever subassemblies 2100 extends through a center point of therespective planet 2102 substantially perpendicular to a radial reference axis RA1 extending from the longitudinal axis LA1 through the center point of therespective planet 2102. - In some embodiments, the
main shaft 1000 includes afirst end portion 1005, acentral portion 1010 and asecond end portion 1015. Thefirst end portion 1005 couples to apower output portion 805 of the torque converter assembly 800 (for example, an output hub of a converter turbine) in a manner precluding relative rotation of themain shaft 1000 with respect to thepower output portion 805. Thecentral portion 1010 of themain shaft 1000 couples to the input load-cam-and-traction-ring subassembly 2000A in a manner precluding relative rotation of themain shaft 1000 with respect to the input load-cam-and-traction-ring subassembly 2000A. Thesecond end portion 1015 of themain shaft 1000 couples to the firstpower input portion 1405 of the combiningdevice 1400 in a manner precluding relative rotation of themain shaft 1000 with respect to the firstpower input portion 1405. The output load-cam-and-traction-ring subassembly 2000B of the variator 1200 couples to a secondpower input portion 1410 of the combiningdevice 1400 in a manner precluding relative rotation of the output load-cam-and-traction-ring subassembly 2000B with respect to the secondpower input portion 1410. Thus, themain shaft 1000 is suitably configured for transferring power from the torque converter subassembly 800 (a) directly to the combiningdevice 1400, and (b) to the combiningdevice 1400 through thevariator 1200. - Each of the
planets 2102 is located by the input load-cam-and-traction-ring subassembly 2000A, the output load-cam-and-traction-ring subassembly 2000B, and the shift-cam-and-sun subassembly 2200. Themain shaft 1000 can be configured to exert torque on the input load-cam-and-traction-ring subassembly 2000A. Through traction at a respective input traction interface TI1 between the input load-cam-and-traction-ring subassembly 2000A and eachplanet 2102, torque is exerted by the input load-cam-and-traction-ring subassembly 2000A on theplanets 2102, thereby causing eachplanet 2102 to rotate about a respective planet axle 2104 (seeFIG. 4 ). The input traction interface TI1 is defined, as used here, at a region of contact between the input load-cam-and-traction-ring subassembly 2000A and therespective planet 2102. - Through traction at a respective output traction interface TI2 between the input load-cam-and-traction-
ring subassembly 2000B and eachplanet 2102, torque is exerted by theplanets 2102 on the output load-cam-and-traction-ring subassembly 2000B, thereby causing the output load-cam-and-traction-ring subassembly 2000B to rotate about themain shaft 1000. The output traction interface TI2 is defined, as used here, at a region of contact between the output load-cam-and-traction-ring subassembly 2000B and therespective planet 2102. As shown inFIG. 3A , the output load-cam-and-traction-ring subassembly 2000B can be coupled to the combiningdevice 1400. Accordingly, torque can be transferred from themain shaft 1000 to the combiningdevice 1400 through thevariator 1200. - As discussed above in reference to
FIGS. 3A and 3B , the ratio of torque transferred to the combiningdevice 1400 through thevariator 1200 or through themain shaft 1000 can be selectively variable dependent upon the torque ratio of thevariator 1200. The torque ratio refers to a relative position of the input traction interface TI1 and the output traction interface TI2, relative to the axis LA2, for a given tilt of the planet-and-shift-lever subassemblies 2100. When the tangential surface velocity of theplanets 2102 at the input traction interface TI1 is the same as the tangential surface velocity of theplanets 2102 at the output traction interface TI2, the torque ratio is substantially equal to 1 and there is no corresponding torque multiplication. Through tilting of the planet-and-shift-lever subassemblies 2100, the ratio of the tangential surface velocity of theplanets 2102 at the input traction interface TI1 to that of the tangential surface velocity of theplanets 2102 at the output traction interface TI2 is selectively adjustable. As discussed further below, the shift-cam-and-sun subassembly can be configured such that translation of the shift-cam-and-sun subassembly 2200 causes such tilt of the planet-and-shift-lever subassemblies 2100. The direction of tilt of the planet-and-shift-lever subassemblies 2100 from the position corresponding to the torque ratio of 1 dictates whether the torque multiplication is greater than 1 (that is, torque output is greater than torque input) or less than 1 (that is, torque input is greater than torque output). - As depicted in
FIGS. 3A and 4 , the input traction interface TI1 and the output traction interface TI2 are angularly equidistant relative to a radial reference axis RA1 extending through the tangential reference axis TA1. As a result, the torque ratio is 1 when a longitudinal axis LA2 of eachplanet 2102 is parallel with the longitudinal axis LA1 of themain shaft 1000. Such an equidistant configuration provides for a balanced adjustment range such that full adjustment of the planet-and-shift-lever subassemblies 2100 in a first adjustment direction results in the same absolute torque multiplication value as full adjustment in a second direction. In other embodiments, the input traction interface TI1 and the output traction interface TI2 may be non-equidistant from the reference axis TA1 when the torque ratio is 1.0 and the longitudinal axis LA2 is parallel with the longitudinal axis LA1. Such a non-equidistant configuration provides for biasing of the adjustment range such that full adjustment of the planet-and-shift-lever subassemblies 2100 in the first adjustment direction results in a different absolute torque multiplication value than full adjustment in the second adjustment direction. - Referring now to FIGS. 3A and 4-6, in one embodiment the
variator 1200 can be axially constrained on themain shaft 1000 between anaxial reaction flange 1020 of themain shaft 1000 and an axial lock nut 1305 (FIG. 4 ). Theaxial lock nut 1305 includes a threaded bore configured for mating with a corresponding threadedportion 1025 of themain shaft 1000. Theaxial reaction flange 1020 can be fixedly attached to themain shaft 1000 adjacent thesecond end portion 1015 of themain shaft 1000. The threadedportion 1025 can be an integral component of themain shaft 1000, adjacent to thecentral portion 1010 of themain shaft 1000. In one embodiment, themain shaft 1000 includes ananti-rock piloting surface 1028 configured for engaging a mating anti-rock piloting surface of theaxial lock nut 1305 for limiting rocking of theaxial lock nut 1305 with respect to themain shaft 1000. - A
first engagement extension 1030 at thefirst end portion 1005 of themain shaft 1000 can be configured for engaging or supporting a bearing assembly 810 (FIG. 3A ) that interfaces with certain components of thetorque converter subassembly 800 or other support member. Asecond engagement extension 1035 at thesecond end portion 1015 of themain shaft 1000 can be configured for engaging or supporting a bearing assembly 1415 (FIG. 3A ) that interfaces with certain components of the combiningdevice 1400. In some embodiments, the bearingassemblies assemblies respective engagement extension - Referring to
FIGS. 5 and 6 , thefirst end portion 1005 of themain shaft 1000 can include torqueconverter engaging splines 1040 configured to couple to mating splines of the power output hub of thetorque converter assembly 800. Thecentral portion 1010 of themain shaft 1000 includes input loadcam engaging splines 1045 configured to couple to mating splines of the input-load-and-traction-ring subassembly 2000A (that is, a power input portion) of thevariator 1200. Thesecond end portion 1015 of themain shaft 1000 can include combiningdevice engaging splines 1050 configured to couple to mating splines of the firstpower input portion 1405 of the combiningdevice 1400. Thus, themain shaft 1000 can be configured for transferring power from thetorque converter subassembly 800 directly to the combiningdevice 1400, and to the combiningdevice 1400 through thevariator 1200. A splined coupling is one example of a coupling suitable for precluding relative rotation of themain shaft 1000 with respect to the power output portion of thetorque converter subassembly 800, the power input portion of thevariator 1200, and the firstpower input portion 1405 of the combiningdevice 1400. However, other couplings can be used. A key and mating engagement coupling is another example of a suitable coupling. - In one embodiment, the
main shaft 1000 can include a first channel 1055 (FIGS. 3A , 4 and 6) for facilitating flow of a transmission fluid from thepower output portion 805 of thetorque converter subassembly 800 to an interface between the main shaft 1000 a transmission oil pump 806 (FIG. 3A ) of thetorque converter subassembly 800. Themain shaft 1000 can include asecond channel 1060 for enabling flow of lubricant to thevariator 1200 and/or to the combiningdevice 1400. - Referring now to
FIGS. 7-14 , in one embodiment the input load-cam-and-traction-ring subassembly 2000A can include aninput load cam 2005A, aninput traction ring 2010A, a plurality of inputload cam rollers 2015A (FIG. 7 ), and an inputload cam shroud 2020A. In one embodiment, theinput load cam 2005A is in splined engagement with themain shaft 1000, thereby facilitating the transfer of torque from themain shaft 1000 to theinput load cam 2005A. Theinput load cam 2005A can be configured to transfer torque to aninput traction ring 2010A via the plurality of inputload cam rollers 2015A. The inputload cam rollers 2015A are engaged between theinput load cam 2005A and theinput traction ring 2010A. Theinput traction ring 2010A can be positioned between the inputload cam rollers 2015A and theplanets 2102. Torque applied to theinput load cam 2005A by themain shaft 1000 is transferred from theinput load cam 2005A to theinput traction ring 2010A through theload cam rollers 2015A. - In one embodiment, the
input load cam 2005A can include a generally bowl-shapedbody 2052A (seeFIGS. 10-11 ) having ahub portion 2054A and aperimeter edge portion 2056A. In one embodiment, thehub portion 2054A includes acentral bore 2058A having internal splines configured for mating with the input load cam engaging splines 1045 (FIG. 5 ) of themain shaft 1000, thereby supporting theinput load cam 2005A and enabling power to be transferred from themain shaft 1000 to thevariator 1200. - In one embodiment, a set of
bi-directional ramps 2060A can be provided in arear face 2062A of theperimeter edge portion 2056A. Theramps 2060A can be configured for receiving one of the inputload cam rollers 2015A (FIG. 7 ) and cooperates with the respective inputload cam roller 2015A for applying an axial force and a tangential force on theinput traction ring 2010A. In other embodiments, a cam roller retainer (not shown) can be provided to receive and support the input load cam rollers 2015. Through such cooperation, rotation of theinput load cam 2005A causes the inputload cam rollers 2015A to urge theinput traction ring 2010A into compressive engagement with theplanets 2102 and to urge theinput traction ring 2010A into rotation about the longitudinal axis LA1 of themain shaft 1000, thereby providing for torque transfer from theinput load cam 2005A to theplanets 2102 via theinput traction ring 2010A. - Referencing
FIGS. 8 and 9 , in one embodiment, theinput traction ring 2010A has a generally annular ring shape with afront face 2061A and a back face 2063A. Theinput traction ring 2010A includes acontact surface 2065A that engages the planets 2102 (one shown inFIG. 7 ). The input traction interface TI1 is the region of contact between thecontact surface 2065A of theinput traction ring 2010A and each one of the planets 2102 (one shown inFIG. 7 ). Through traction at each input traction interface TI1 torque imparted to theinput traction ring 2010A by theinput load cam 2005A is transferred to theplanets 2102, thereby causing eachplanet 2102 to rotate about therespective planet axle 2104. Preferably, but not necessarily, traction at each input traction interface TI1 is provided through an elastohydrodynamic layer formed by a traction fluid. Thecontact surface 2065A is generally angled relative to thefront face 2061A, such that the profile of thecontact surface 2065A mates efficiently with a curvature of eachplanet 2102. The angle of inclination between thefront face 2061A and thecontact surface 2065A can be between about 5 degrees and 75 degrees, more preferably between about 15 degrees and 65 degrees, even more preferably between about 30 degrees and 55 degrees, and most preferably between about 35 degrees and 50 degrees. - The back face 2063A can include a
radiused groove 2067A configured for receiving theload cam rollers 2015A to facilitate torque transfer from theinput load cam 2005A to theinput traction ring 2010A. It is disclosed herein that an input traction ring can include the set of bi-directional ramps, and an input load cam can include the radiused groove. In other embodiments, the input traction ring and the input load cam both have ramps. - Referring to
FIGS. 12-14 , in some embodiments, radially extendingribs 2064A can be attached to afront face 2066A of thebody 2052A, extending generally from theperimeter edge portion 2056A to thehub portion 2054A. A cylindrically shapedflange 2068A extends from thefront face 2066A. The cylindrically shapedflange 2068A intersects theradially extending ribs 2064A. Theradially extending ribs 2064A and the cylindrically shapedflange 2068A jointly and individually enhance stiffness of the bowl-shapedbody 2052A and serve as cooling fins for dissipating heat. Furthermore, in some embodiments, theradially extending ribs 2064A can be used to facilitate the sensing of rotational speed of theinput load cam 2005A. - Referencing
FIGS. 11 , 12, and 14, arecess 2070A in afront face 2071A of thehub portion 2054A is configured for receiving ananti-rocking device 2072A (FIG. 12 ) such as, for example, a bushing, a bearing or a sleeve, which serves to limit rocking of theinput load cam 2005A with respect to themain shaft 1000. Apreloading spring recess 2076A and athrust bearing recess 2078A are provided in arear face 2079A of thehub portion 2054A. Thepreload spring recess 2076A is configured for receiving apreloading spring 2083A (FIG. 7 ), and thethrust bearing recess 2078A is configured for receiving a thrust bearing 2085A (FIG. 7 ). Jointly, such a preloading spring and thrust bearing arrangement serves to exert a reactive preload force between the inputload cam assembly 2000A, the stator-manifold subassembly 2300 and the outputload cam assembly 2000B when thepreloading spring 2083A is compressed. Examples of thepreloading spring 2083A include, but are not limited to, a Bellville washer, a wavy washer, a helical compression spring and other suitably configured spring members. Examples of thethrust bearing 2085A include, but are not limited to, a roller thrust bearing, a thrust bushing, and other devices suitably configured for carrying a thrust load. - Referring now to
FIGS. 7 , 12, 14, 15 and 16, a plurality ofdowel pin holes 2069A (FIGS. 12 and 14 ) in thefront face 2071A can be configured for receiving one or more dowel pins (not shown) to facilitate coupling of the axial lock nut 1305 (FIGS. 7 , 15 and 16) to theinput load cam 2005A for preventing unintentional loosening of theaxial lock nut 1305. As shown inFIGS. 15 and 16 , theaxial lock nut 1305 can have a threadedbore 1306 configured for engaging the corresponding threadedportion 1025 of themain shaft 1000. In on embodiment, theaxial lock nut 1305 can be provided with a polygonal-shaped (for example, hexagonal)outer periphery portion 1307 configured to engage a tool for manipulating theaxial lock nut 1305. A plurality of notches 1309 (for example, dowel engaging features) can be provided in theouter periphery portion 1307 for engaging dowels (not shown) received within one of the dowel pin holes 2069A. Such engagement facilitates selective angular positioning and constraining of theaxial lock nut 1305 with respect to theload input cam 2005A, which is useful for preventing unintentional loosening of theaxial lock nut 1305. Acircumferential groove 1311 exposed at anexterior surface 1312 of theaxial lock nut 1305 can be configured to receive a retaining device (not shown) such as, for example, a snap ring to retain the one or more dowels within respective ones of the dowel pin holes 2069A. When engaged within thecircumferential groove 1311, the retaining device prevents the dowels from unintentionally backing out of the respective dowel pin holes 2069A. Anextension portion 1313 of theaxial lock nut 1305 includes an anti-rock piloting surface 1315 (that is, a reaction surface) that engages the mating anti-rock piloting surface 1028 (FIG. 5 ) of themain shaft 1000 for limiting rocking of theaxial lock nut 1305 with respect to themain shaft 1000. - As shown in FIGS. 7 and 10-14, the input
load cam shroud 2020A includes a bowl-shapedbody 2082A havingperimeter flanges 2084A. The inputload cam shroud 2020A is mountable over thefront face 2066A of theinput load cam 2005A. When so mounted, each one of theperimeter flanges 2084A can be positioned between a respective adjacent pair of theradially extending ribs 2064A, and thehub portion 2054A is exposed within acentral opening 2086A of thebody 2082A. Theradially extending ribs 2064A can include a recessedportions 2088A (FIG. 12 ) that receives ashoulder 2090A (FIG. 12 ) extending between adjacent ones of theperimeter flanges 2084A. The inputload cam shroud 2020A can be mounted on theinput load cam 2005A to, among other things, reduce the potential for theradially extending ribs 2064A to generate unwanted fluid dynamics (for example, air and/or lubricant drag). -
FIGS. 17-19 show an alternative embodiment of an input load cam, which is referred to herein as theinput load cam 3005A. Theinput load cam 3005A is suitably configured for being used in place of theinput load cam 2005A discussed above with reference to FIGS. 4 and 13-14. Theinput load cam 3005A includes a generally bowl-shapedbody 3052A having ahub portion 3054A and aperimeter edge portion 3056A. In some embodiments, thebody 3052A has a conical shape. Thehub portion 3054A can include acentral bore 3058A having splines configured to mate with splines of thecentral portion 1010 of the main shaft 1000 (FIG. 4 ), thereby facilitating power transfer from themain shaft 1000 to thevariator 1200. A set ofbi-directional ramps 3060A can be provided in arear face 3062A of theperimeter edge portion 3056A. Theramps 3060A can be configured for receiving the inputload cam rollers 2015A (FIG. 7 ) and to cooperate with the inputload cam rollers 2015A for applying an axial force and a tangential force on theinput traction ring 2010A. Through such cooperation, theramps 3060A facilitate torque transfer from theinput load cam 3005A to theinput traction ring 2010A. -
Radial fins 3064A can be attached to afront face 3066A of thebody 3052A, extending outwardly from theperimeter edge portion 3056A. Theradial fins 3064A serve, among other things, as cooling fins for dissipating heat. Furthermore, theradial fins 3064A can be used for facilitating the sensing of the rotational speed of theinput load cam 3005A. The inputload cam shroud 2020A ofFIGS. 10-12 is compatible with theinput load cam 3005A. The inputload cam shroud 2020A can be mounted on theinput load cam 3005A; however, in some embodiments, the inputload cam shroud 2020A is not used. - A
recess 3070A (FIGS. 11 , 12 and 14) in afront face 3071A of thehub portion 3054A can be configured for receiving an anti-rock device such as, for example, the anti-rock device 3072A shown inFIG. 12 . Apreloading spring recess 3076A and athrust bearing recess 3078A are provided in arear face 3079A of thehub portion 3054A. Thepreloading spring recess 3076A is configured for receiving thepreloading spring 2083A (FIG. 7 ), and thethrust bearing recess 3078A is configured for receiving the thrust bearing 2085A (FIG. 7 ). Jointly, such a preloading spring and thrust bearing arrangement serves to, among other things, exert a reactive preload force between the inputload cam assembly 2000A, the stator-manifold subassembly 2300, and the outputload cam assembly 2000B. A plurality ofdowel pin holes 3069A (FIGS. 18 and 19 ) in thefront face 3071A can be configured for receiving dowel pins (not shown) to facilitate coupling of the axial lock nut 1305 (FIGS. 7 , 15 and 16) to theinput load cam 3005A for preventing unintentional loosening of theaxial lock nut 1305. - Referring now to
FIGS. 20-26 the output load-cam-and-traction-ring subassembly 2000B can include anoutput load cam 2005B, anoutput traction ring 2010B, a plurality of outputload cam rollers 2015B (FIG. 20 ), an outputload cam shroud 2020B, an output loadcam bearing assembly 2022B, and abearing support adapter 2024B. Theoutput load cam 2005B can be mounted on themain shaft 1000 through use of the output loadcam bearing assembly 2022B and thebearing support adapter 2024B. As shown inFIG. 20 , the output loadcam bearing assembly 2022B fits between theoutput load cam 2005B and thebearing support adapter 2024B. In one embodiment, the output loadcam bearing assembly 2022B can be axially constrained by corresponding structural features of theoutput load cam 2005B and thebearing support adapter 2024B. - Referencing
FIGS. 25-26 , in one embodiment, thebearing support adapter 2024B can include acentral bore 2025B configured for engaging a mating surface 1065 (FIGS. 5 and 20 ) of themain shaft 1000. The bearing support adapter can include ashoulder 2026B configured to abut against theaxial reaction flange 1020 of themain shaft 1000 to react axial loads that arise in thevariator 1200. Theshoulder 2026B is accessible through afirst face 2016B of thebearing support adapter 2024B. The bearingadapter 2024B can be mounted on themain shaft 1000 by, for example, an interference fit, press fit, or close tolerance clearance fit with themating support surface 1065 of themain shaft 1000. Aflange 2027B of thebearing support adapter 2024B can be adapted to react axial loads from the output loadcam bearing assembly 2022B. In one embodiment, thebearing support adapter 2024B can include a piloting surface 2029B that pilots on, or alternatively provides clearance with respect to, theaxial reaction flange 1020. Thebearing support adapter 2024B can include arecess 2077B for receiving and supporting aspring 2087B (seeFIG. 20 ). Thespring 2087B can be a Bellville spring for providing preloading. - A bearing
support surface 2028B of thebearing support adapter 2024B can be configured to support the output loadcam bearing assembly 2022B. Thebearing support adapter 2024B can include apreloading spring recess 2076B and athrust bearing recess 2078B, which are both accessible through asecond face 2018B of thebearing support adapter 2024B. Thepreloading spring recess 2076B is configured for receiving apreloading spring 2083B (FIG. 20 ), and thethrust bearing recess 2078B is configured for receiving a thrust bearing 2085B (FIG. 20 ). Jointly, such a preloading spring and thrust bearing arrangement serves to exert a reactive preload force between the inputload cam assembly 2000A, the stator-manifold subassembly 2300, and the outputload cam assembly 2000B, when thepreloading spring 2083B is compressed. Examples of thepreloading spring 2083B include, but are not limited to, a Bellville washer, a wavy washer, a helical compression spring, and other suitably configured spring members. Examples of thethrust bearing 2085B include, but are not limited to, a roller thrust bearing, a thrust bushing, and other devices suitably configured for carrying a thrust load. In some embodiments, thethrust bearing recess 2078B receives a bearing race adapted to cooperate with a needle bearing, which couples to a bearing race 4243 that is integral with, or positioned adjacent to, the stator 4200 (seeFIG. 56 ). - In one embodiment, the
output load cam 2005B is coupled to theoutput traction ring 2010B via the outputload cam rollers 2015B, which can be positioned between theoutput load cam 2005B and theoutput traction ring 2010B. Theoutput traction ring 2010B is placed between the outputload cam rollers 2015B and theplanets 2102. Torque exerted on theoutput traction ring 2010B by theplanets 2102 is transferred from theoutput traction ring 2010B to theoutput load cam 2005B through theload cam rollers 2015B. - In some embodiments, the
output load cam 2005B can include a generally bowl-shapedbody 2052B having ahub portion 2054B and aperimeter edge portion 2056B. Thehub portion 2054B includes acentral bore 2058B havingsplines 2059B configured to mate with splines of the secondpower input portion 1410 of the combining device 1400 (FIG. 3A ), thereby facilitating power transfer from thevariator 1200 to the combiningdevice 1400. Thehub portion 2054B can also include abearing recess 2057B configured for receiving an outer race of the output loadcam bearing assembly 2022B (FIG. 20 ). - A set of
bi-directional ramps 2060B is provided in arear face 2062B of theperimeter edge portion 2056B. Theramps 2060B can be configured for receiving the outputload cam rollers 2015B (FIG. 20 ) and for cooperating with the outputload cam rollers 2015B for, among other things, applying an axial force on theoutput traction ring 2010B. Through such cooperation, rotation of theoutput traction ring 2010B causes the outputload cam rollers 2015B to urge theoutput traction ring 2010B into compressive engagement with theplanets 2102 and to urge theoutput load cam 2005B into rotation about the longitudinal axis LA1 of themain shaft 1000, thereby providing for torque transfer from theplanets 2102 to theoutput load cam 2005B.Radially extending ribs 2064B can be attached to afront face 2066B of thebody 2052B, extending generally from theperimeter edge portion 2056B to thehub portion 2054B. Theradially extending ribs 2064B enhance stiffness of thebody 2052B and serve as cooling fins for dissipating heat, among other things. Furthermore, the radially extending ribs 2064 can be used for facilitating the sensing of rotational speed of theoutput load cam 2005B. In some embodiments, theoutput load cam 2005B can include ahub portion 2054B configured to engage the secondpower input portion 1405 of the combiningdevice 1400 in a manner precluding relative rotation of theoutput load cam 2005B with respect to the secondpower input portion 1405. In this manner, the interface between theoutput load cam 2005B and the secondpower input portion 1405 enables power transfer from thevariator 1200 to the combiningdevice 1400. - As shown in
FIGS. 20 and 24 , in one embodiment, the outputload cam shroud 2020B can include a bowl-shapedbody 2082B havingperimeter flanges 2084B. The outputload cam shroud 2020B is mountable over thefront face 2066B of theoutput load cam 2005B. When so mounted, each one of theperimeter flanges 2084B is positioned between a respective adjacent pair of theradially extending ribs 2064B, and thehub portion 2054B of theoutput load cam 2005B is exposed within acentral opening 2086B of thebody 2082B. Theradially extending ribs 2064B can include a recessedportions 2088B (FIG. 24 ) that receiveshoulders 2090B extending between adjacent ones of theperimeter flanges 2084B. Theshroud 2020B can be mounted on theoutput load cam 2005B to, among other things, reduce the potential for theradially extending ribs 2064B to generate undesired fluid dynamics. -
FIGS. 27-29 show an alternative embodiment of an output load cam, which is referred to herein as theoutput load cam 3005B. Theoutput load cam 3005B is suitably configured for being used in place of theoutput load cam 2005B discussed above in reference to FIGS. 4 and 20-23. In one embodiment, theoutput load cam 3005B includes a generally bowl-shapedbody 3052B having ahub portion 3054B and aperimeter edge portion 3056B. Thehub portion 3054B includes acentral passage 3058 B having splines 3059B configured to mate external splines of the secondpower input portion 1405 of the combiningdevice 1400, thereby facilitating power transfer from thevariator 1200 to the combiningdevice 1400. In one embodiment, thehub portion 3054B can also include abearing recess 3057B configured for receiving an outer race of the output loadcam bearing assembly 2022B (FIG. 20 ). In some embodiments, a set ofbi-directional ramps 3060B can be provided in arear face 3062B of theperimeter edge portion 3056B. Theramps 3060B can be configured for receiving the outputload cam rollers 2015B (FIG. 20 ) and to cooperate with the outputload cam rollers 2015B for applying an axial force on theoutput traction ring 2010B and theoutput load cam 3005B. Through such cooperation, theramps 3060B enable torque transfer from theoutput traction ring 2010B to theoutput load cam 3005B. In some embodiments,radial fins 3064B are attached to afront face 3066B of thebody 3052B, extending outwardly from theperimeter edge portion 3056B. Theradial fins 3064B serve as cooling fins for dissipating heat. Furthermore, theradial fins 3064B can be used for facilitating the sensing of rotational speed of theoutput load cam 3005B. Theshroud 2020B ofFIG. 24 is compatible with theoutput load cam 3005B. Theshroud 2020B can be mounted on theoutput load cam 3005B to, among other things, reduce the potential for theradial fins 3064B to generate undesirable fluid dynamics. - Referring now to
FIGS. 30-33 , in one embodiment, each one of the planet-and-shift-lever subassemblies 2100 includes aplanet 2102 rotatably mounted on aplanet axle 2104, which can be positioned on a planetcentral bore 2103. Spaced apartplanet bearings 2108, aninner spacer 2110, andouter spacers 2112 can mount coaxially on theplanet axle 2104. In some embodiment, theinner spacer 2110 is positioned between theplanet bearings 2108, and each one of theplanet bearings 2108 is positioned between a respective one of theouter spacers 2112 and theinner spacer 2110. Accordingly, eachplanet 2102 is rotatably mounted on arespective planet axle 2104 in a load-bearing and rotatable manner. It is disclosed herein that the present invention is not limited to a particular planet bearing and spacer arrangement for rotatably mounting eachplanet 2102 on therespective planet axle 2104. For example, in some embodiments, a planet bearing and spacer arrangement using more than two or less two planet bearings and more than two or less spacers (that is, inner position and/or outer position) can be implemented. - Planet axle shift levers 2106 (“
shift levers 2106”) can be fixedly attached to opposingend portions 2107 of theplanet axle 2104 such that theplanet 2102 is positioned between theshift levers 2106. Theplanet axle 2104 extends through a planet axle bore 2111 (seeFIGS. 32 and 33 ) of eachshift lever 2106. In one embodiment, the opposingend portions 2107 include askew roller shoulders 2109 on which skewrollers 2122 mount. Eachskew roller 2122 can be held in place by awasher 2124 and aclip ring 2126, whichclip ring 2126 can be engaged within a groove in theskew roller shoulder 2109. It is disclosed herein that, in some embodiments, ashift lever 2106 can include one or more features (not shown) such as, for example, a recess, a channel, etc., for providing clearance with other components of thevariator 1200. - As shown in
FIGS. 30-33 , in some embodiments, a shiftguide roller axle 2116 can be engaged within a shift guide roller axle bore 2117 (FIG. 33 ) of eachshift lever 2106 and within a corresponding axle capturing feature 2119 (FIGS. 32 and 33 ) of theplanet axle 2104. In one embodiment, the shift guideroller axle bore 2117 intersects and is generally perpendicular to theplanet axle bore 2111. The shift guideroller axle bore 2117 is adjacent to afirst end portion 2121 of theshift lever 2106. Examples of theaxle capturing feature 2119 include, but are not limited to, a feature generally characterized as a notch, a cut out, a channel, a seat, or the like. The shiftguide roller axle 2116 and the correspondingaxle capturing feature 2119 can be configured for limiting (for example, substantially precluding) radial displacement of the shiftguide roller axle 2116 with respect to the engagedaxle capturing feature 2119. Thus, such mating configuration of the shiftguide roller axle 2116 and the correspondingaxle capturing feature 2119 limits displacement of theshift lever 2106 along the longitudinal axis LA2 of theplanet axle 2104 when the shiftguide roller axle 2116 is mounted on theplanet axle 2104 with the shiftguide roller axle 2116 engaged within the shift guideroller axle bore 2117 and the corresponding axle capturing feature 2119 (FIGS. 32 and 33 ).Shift guide rollers 2114 can be mounted on opposing end portions of each shiftguide roller axle 2116. Each shift guideroller axle 2116 can be secured in place by, for example,washers 2118 and clip rings 2120, which clip rings 2120 can be engaged within agroove 2191 of the shiftguide roller axle 2116. In other embodiments, the shiftguide roller axle 2116 can be secured by, for example, an interference fit, press fit, etc. - At a
second end portion 2125 of each shift levers 2106, aroller receiving channel 2129 is provided. Ashift cam roller 2128 is positioned in theroller receiving channel 2129. A shiftcam roller axle 2130 extends through theshift cam roller 2128 and into engagement with axle receiving passages 2131 (FIG. 33 ). The shiftcam roller axle 2130 can be secured in place through an interference fit with the respectiveaxle receiving passages 2131. In other embodiments, securing means such as a clip and groove arrangement can be implemented. - Referring to
FIGS. 32-35 , in one embodiment, theplanet axle 2104 can have a throughcentral bore 2134 andtransverse channels 2142 in a substantiallycylindrical body 2132. Thetransverse channels 2142, among other things, enable fluid communication between thecentral bore 2134 and the space external of theplanet axle 2104, thereby allowing for lubrication of thebearings 2108. Theskew roller shoulders 2109, which are provided for receiving theskew rollers 2122, are defined by a reduction in diameter of thecylindrical body 2132.Grooves 2140 are provided in theskew roller shoulders 2109 for receiving the clip rings 2126 that constrain the skew rollers 2122 (FIG. 32 ). It is disclosed herein that, in other embodiments, thecylindrical body 2132 has a generally uniform diameter from over its entire length, such that reduction in diameter defining theskew roller shoulders 2109 is omitted and theskew rollers 2122 are corresponding configured for mating with uniform diameter of thecylindrical body 2132. - Referring to FIGS. 30 and 37-43, in one embodiment, the shift-cam-and-
sun subassembly 2200 can includesun 2202,bearings 2204,shift cams 2206,control pistons 2208,piston tube 2210,shim 2212,inner seals 2214, andouter seals 2216. As shown inFIGS. 30 , 37 and 38, in some embodiments, thecontrol pistons 2208 are coupled to theshift cams 2206 through thepiston tube 2210. Thecontrol pistons 2208 and theshift cams 2206 can be mounted on thepiston tube 2210 by, for example, a press-fit interface. Thesun 2202 can be operationally coupled to theshift cams 2206 through thebearings 2204. Thebearings 2204 can be configured to transfer axial and radial loads between thesun 2202 and theshift cams 2206. Thesun 2202 and theshift cams 2206 can be configured to receive thebearings 2204. The inventive embodiments are not limited to bearings of a particular type. For example, an angular contact bearing is a suitable bearing type for thebearings 2204. - In one embodiment, the
shim 2212 is positioned between theshift cams 2206 for setting a desired axial clearance between thesun 2202 and theshift cams 2206. Such clearance facilitates relative rotation between theshift cams 2206 and thesun 2202 without allowing contact between adjacent surfaces. In other embodiments, a plurality of shims can be used for achieving the desired clearance between thesun 2202 and theshift cams 2206. In still other embodiments, theshim 2212 can be omitted and theshift cams 2206 and/orsun 2202 can be manufactured in a manner to achieve suitable clearance between thesun 2202 and theshift cams 2206. - As shown in
FIGS. 37-39 , in one embodiment, thesun 2202 can have abody 2218 having a generally cylindrical outer diameter andinternal recesses 2222 for receiving thebearings 2204. As shown, thesun 2202 can have acentral shoulder 2220 that facilitates axial constraint of thebearings 2204, thereby limiting an insertion depth of each one of thebearings 2204 within the respective one of therecesses 2222. The inventive embodiments are not limited to particular ways for positioning thebearings 2204 with respect to thebody 2218. For example, in other embodiments, abearing 2204 has an outer race with an integral positioning flange that engages anexterior edge face 2223 of thesun 2202. In still other embodiments, therecesses 2222 have a tapered face and each one of thebearings 2204 has an outer race with a tapered exterior surface that engages the tapered face of the respective one of therecesses 2222. In still other embodiments, a discrete spacer can be used to facilitate proper spacing between thebearings 2204. In yet other embodiments, the outer races of thebearings 2204 can be formed integral with thesun 2202, and/or the inner races of thebearing 2204 can be formed integral with theshift cam extensions 2206. - As shown in
FIGS. 37 , 38, 40 and 40A, in one embodiment, theshift cam 2206 can include ashift cam profile 2224, which are adapted to guide the motion of theshift cam rollers 2128. One embodiment of data points defining a shape of theshift cam profile 2224 is shown in the table ofFIG. 41 . The X-dimension refers to an axial distance between areference surface 2225 and theshift cam profile 2224. The Y-dimension refers to a radial distance between a longitudinal centerline axis of acentral bore 2228 of theshift cam 2206 and theshift cam profile 2224. In some embodiments, theshift cam 2206 includes ashift cam extension 2226 having anexterior face 2227 configured to receive a respective one of thebearings 2204, and having aninterior face 2229 configured to engage anexterior face 2252 of thepiston tube 2210. Preferably, but not necessarily, theshift cam extension 2226 includes a lubricationflow enhancing feature 2232 such as, for example a cut-out or notch. In one embodiment, arear face 2230 of theshift cam 2206 opposite to theshift cam profile 2224 is configured to be slightly angled relative to thereference surface 2225 for, among other things, promoting the flow of lubricant in the general area of thebearings 2204 and to maintain a desired clearance between therear face 2230 of theshift cam 2206 and the exterior surfaces 2223 (FIG. 39 ) of thesun 2202. - As shown in
FIGS. 37 , 38 and 42, in one embodiment, acontrol piston 2208 has acentral bore 2249 configured for engaging an exterior face 2254 (FIGS. 37 and 38 ) of thepiston tube 2210. In some embodiments, thecontrol piston 2208 has aninternal recess 2250 and anexternal neck 2248 each configured for receiving and supporting theinner seal 2214 and theouter seal 2216, respectively. Thecontrol piston 2208 has apiston face 2240 on which control fluid pressure exerts force. In one embodiment, thecontrol piston 2208 includes a number ofrecesses 2242, wherein arecess 2242 can be configured to provide clearance for the second end portion 2125 (FIG. 33 ) of arespective shift lever 2106. Side faces 2244 of therecess 2242 can be configured to substantially constrain movement of thesecond end portion 2125 of theshift lever 2106, thereby limiting rotation of therespective shift lever 2106 about the longitudinal axis LA1 of thevariator 1200. In some embodiments, the contoured shape of therecess 2242 can be used as a detectable proximity surface that facilitates the determination of a relative position of thecontrol piston 2208 with respect to the longitudinal axis LA1. An anti-rotation feature 2246 (for example, a groove, pin, seat slot, etc.) can be provided in an exterior face of thecontrol piston 2208 for engaging a mating anti rotation feature of an adjacent variator component to limit rotation of thecontrol piston 2208 about the longitudinal axis LA1. - As shown in
FIGS. 38 and 43 , in one embodiment, thepiston tube 2210 can include exterior faces 2252, 2254 and acentral bore 2256. Thefaces 2252 can be configured to receive theshift cams 2206, and thefaces 2254 can be configured to receive thecontrol pistons 2208. The outside diameter of thefaces 2254 is nominally the same as each other, and the outside diameter of thefaces 2252 are nominally the same as each other. In one embodiment, the outside diameter of thefaces 2252 is slightly smaller than the outside diameter of thefaces 2252, which precludes having to press fit theshift cams 2206 over the respectiveouter engagement surface 2252 prior to press fitting it onto the respectiveinner engagement surface 2254. As is discussed further below, thecentral bore 2256 can be configured to receive mating portions of astator FIG. 44 ) therein. Preferably, but not necessarily, thepiston tube 2210 has a shim receiving recess 2260 (for example, a circumferential groove) for receiving a portion of the shim 2212 (FIG. 38 ) and has anorifice 2259 for allowing passage of lubricant. Preferably, but not necessarily, theorifice 2259 is exposed within theshim receiving recess 2260. - Referring now to
FIGS. 44-46 , in one embodiment, the stator-manifold subassembly 2300 includes acenter manifold 4000, afirst stator 4200A, asecond stator 4200B, afirst oil galley 4400A and asecond oil galley 4400B. Thefirst stator 4200A attaches to afirst side face 4005 of thecenter manifold 4000, and thesecond stator 4200B attaches to asecond side face 4010 of thecenter manifold 4000. Thefirst oil galley 4400A mounts on thefirst stator 4200A, and thesecond oil galley 4400B mounts on thesecond stator 4200B. As used here, the terms “oil”, “lubricant”, “lubricating fluid,” and “traction fluid” are generally interchangeable. Where appropriate, it will be clear by the context that the fluid, or condition, refers to lubrication rather than traction. - In one embodiment, the
center manifold 4000 is configured for, among other things, facilitating the stator-manifold subassembly 2300 being fixedly mounted to thetransmission housing 1800 of the transmission 600 (FIG. 3A ), supporting thestators FIGS. 3A and 44 ), and housing and supporting various sensors. Examples of such sensors include, but are not limited to, sensors for sensing lubricant temperature, pressure, and viscosity. In some embodiments, a sensor is provided for sensing the position of theshift lever subassembly 2100 relative to a surface on thestator 4200. - The
stators lever subassemblies 2100, supporting the shift-cam-and-sun subassembly 2200, and communicating control and traction fluids. As discussed below, the planet-and-shift-lever subassemblies 2100 are each movably supported jointly by thestators sun subassembly 2200. The shift-cam-and-sun subassembly 2200 cooperates with thestators lever subassemblies 2100. Theoil galleys lever subassemblies 2100, the shift-cam-and-sun subassembly 2200, and other components of thevariator 1200. - Referring now to
FIGS. 44-53 , thecenter manifold 4000 includes abase plate 4015 and acover plate 4020. Thebase plate 4015 includes afirst side face 4016A and asecond side face 4016B, and thecover plate 4020 includes afirst side face 4021A and asecond side face 4021B. In one embodiment, theplates plates out pattern 4025 configured to generally surround the array of planet-and-shift-lever subassemblies 2100 (FIG. 44 ). Theplates FIGS. 44-48 with the cut-out pattern of thebase plate 4015 being aligned with the cut-out pattern of thecover plate 4020. Thesecond side face 4016B of thebase plate 4015 abuts thefirst side face 4021A of thecover plate 4020 when theplates - A first
sensor cable groove 4027 and a secondsensor cable groove 4029 can be provided in thefirst side face 4016A of thebase plate 4015. Example sensors corresponding to such sensor cables include, but are not limited to, a gamma sensor, a fluid temperature sensor, and a speed measuring device sensor. Thebase plate 4015 includes bolt holes 4030 (FIGS. 47 , 49 and 50), and thecover plate 4020 includes bolt holes 4031 (FIGS. 48 , 52 and 53), which bolt holes 4030, 4031 are configured to receive bolts (not shown) for securing theplates plates - As shown in
FIGS. 47-49 , 52 and 53, theplates dowel pin holes 4035 of thebase plate 4015 and thedowel pin holes 4035 of thecover plate 4020 are located in the same relative positions with respect to the cut-out pattern 4025. Thedowel pin holes 4035 can be located radially in line withlubricant ports respective plate base plate 4015 with thecover plate 4020. - In one embodiment, the
base plate 4015 includes a footing 4040 (seeFIGS. 45-46 and 49-50) configured for cooperating with the transmission housing 1800 (FIG. 3A ) to provide torque reaction at thefooting 4040, thereby limiting movement of thebase plate 4015 with respect to thetransmission housing 1800.Bolt holes 4043 receive bolts (not shown) for fastening thebase plate 4015 to thetransmission housing 1800. In some embodiments, thebase plate 4015 includes locatingpads 4045 that engage a mating structure (for example, a conformingly shaped recess, protruding ridge, etc.) of thetransmission housing 1800. Thelocating pads 4045 facilitate locating thebase plate 4015 in thetransmission housing 1800. - As shown in
FIGS. 45 , 47, and 49, in some embodiments, opposing ones of thelocating pads 4045 include acam wedge base 4050 that cooperates with a corresponding cam dowel 4055 (see FIGS. 45 and 51A-51B) for fixedly engaging (for example, pressing) thebase plate 4015 and/or thecover plate 4020 against one or more mating features of thetransmission housing 1800. Thecam wedge base 4050 is a generally flat surface that is angled with respect to thefirst side face 4016A of thebase plate 4015. Through such engagement, thecenter manifold 4000 can be positioned and, additionally, torque reaction can be provided adjacent one or more of thelocating pads 4045 for limiting movement of thebase plate 4015 with respect to thetransmission housing 1800. - As best shown in
FIGS. 47-48 and 51A-51B, acam dowel 4055 includes a generally cylindrical shapedcam body 4057 having afirst end portion 4065 and asecond end portion 4067. Thefirst end portion 4065 includes acam wedge 4069 and thesecond end portion 4067 has a generally flat face 4070 (that is, extending generally perpendicular to a longitudinal reference axis of the cam body 4057). Thecam wedge 4069 includes a face that is skewed with respect to the longitudinal reference axis of thecam body 4057. Preferably, but not necessarily, the face of thecam wedge 4069 is generally flat. Preferably, but not necessarily, a threadedbore 4072 extends from theflat face 4070 at least partially toward thesecond end portion 4067. In use, for example, thecam dowel 4055 resides within a threaded passage in a wall of thetransmission housing 1800, with thecam wedge 4069 extending from within the threaded passage into engagement with thecam wedge base 4050. Thecam dowel 4055 can be forced against thecam wedge base 4050 using, for example, a setscrew engaged within the threaded passage within the wall of thetransmission housing 1800. Through such forced engagement between the tapered faces of thecam wedge 4069 and thecam wedge base 4050, thecenter manifold 4000 bears against a mating feature of thetransmission housing 1800, thereby limiting movement of thecenter manifold 4000 with respect to thetransmission housing 1800. The threadedbore 4072 provides for engagement with a threaded extractor device for facilitating removal of thecam dowel 4055 from a passage of thetransmission housing 1800. - In one embodiment, the
plates stators FIG. 3A , which is advantageous in that it obviates the need to segregate such fluids. - Referring to
FIGS. 47-53 , in some embodiments, thebase plate 4015 can include lubricant flow passages (not shown) that extend between a respectivelubricant inlet port 4076 and a respectivelubricant outlet port 4084, thereby facilitating lubricant flow between correspondinglubricant inlet ports 4076 andlubricant outlet ports 4084. In one embodiment, thelubricant inlet ports 4076 receive lubricant from a lubrication fluid pump apparatus (not shown) of thetransmission 600 or a standalone lubrication fluid pump apparatus. In some embodiments, thebase plate 4015 can include a first control fluid passage (not shown) that extends between a first controlfluid inlet port 4078 and a first controlfluid outlet port 4091 to allow flow of control fluid between the first controlfluid inlet port 4078 and the first controlfluid outlet port 4091. Thebase plate 4015 can also include a second control flow passage (not shown) that extends between a second controlfluid inlet port 4080 and a second controlfluid outlet port 4092 to allow flow of control fluid between the second controlfluid inlet port 4080 and the second controlfluid outlet port 4092. - In one embodiment, each
lubricant inlet port 4076, the first controlfluid inlet port 4078, and the second controlfluid inlet port 4080 are located in abottom edge face 4082 of thefooting 4040, as shown inFIG. 50 . The controlfluid outlet ports base plate 4015. A firstcontrol fluid port 4093 of the cover plate 4020 (FIGS. 52 and 53 ) aligns with the first controlfluid outlet port 4091 of thebase plate 4015, and a secondfluid control port 4094 of thecover plate 4020 aligns with the second controlfluid outlet port 4092 of thebase plate 4015 when theplates - In one embodiment, the
center manifold 4000 can be configured so that lubricant flows from thelubricant inlet ports 4076 to the respectivelubricant outlet ports 4084 and then into a lubricant distribution channel 4085 (FIG. 52 ) in thefirst side face 4021A of thecover plate 4020. Thelubricant distribution channel 4085 extends at least partially around a perimeter region of thecover plate 4020.Branch lubricant channels 4086 extend between thelubricant distribution channel 4085 andlubricant ports 4087 and/or between thelubricant distribution channel 4085 and a respectivelubricant spray port 4088. Thelubricant ports 4087 communicate with fluid passages (not shown) that extend between the side faces 4021A, 4021B of thecover plate 4020. Thelubricant ports 4087 align withlubricant ports 4089 when theplates first stator 4200A to receive lubricant from thelubricant ports 4089, and thesecond stator 4200B to receive lubricant from thelubricant ports 4087. - A spray of lubricant can be provided from the
lubricant spray ports 4088 of thecover plate 4020, which can be directed at, for example, the output traction interface TI2 (FIG. 44 ) between theoutput traction ring 2010B and the planets 2102 (one shown inFIG. 44 ). Similarly, thebase plate 4015 can include lubricant spray ports 4090 (seeFIG. 49 ) that each aligns with thelubricant distribution channel 4085 and/or a respective one of thebranch lubricant channels 4086, thereby facilitating the provision of a spray of lubricant from thelubricant spray ports 4090, which can be directed at, for example, the input traction interface TI1 (FIG. 44 ) between theinput traction ring 2010A and the planets 2102 (one shown inFIG. 44 ). - In one embodiment, the control fluid passages (not shown) extending between the control
fluid inlet ports fluid outlet ports transmission 600 or stand alone apparatus. Through such independent and selective communication, a pressure differential between the control fluid passages can be produced. As discussed further below, selective control of this pressure differential facilitates selective adjustment of a position of the shift-cam-and-sun subassembly 2200 (FIG. 44 ) with respect to the longitudinal axis LA1 of themain shaft 1000. - As shown in
FIGS. 45 and 46 , thestators stator 4200. Referring toFIGS. 45 , 46 and 54-59, in one embodiment, thestator 4200 can include a number of shiftlever guide flanges 4202, a plurality ofstator extensions 4204, and acontrol piston receiver 4206. In one embodiment, the shiftlever guide flanges 4202 attach to thecontrol piston receiver 4206 in a radially extending and uniformly angularly spaced manner. Aplanet axle passage 4208 extends between each adjacent pair of shiftlever guide flanges 4202. Thestator extensions 4204 extend axially from afirst side face 4210 of each shiftlever guide flange 4202. Thecontrol piston receiver 4206 extends axially from asecond side face 4212 of each shiftlever guide flange 4202. Preferably, but not necessarily, the shiftlever guide flanges 4202, thestator extensions 4204, the control piston receiver 4206A, and theplanet axle passages 4208 are uniformly spaced and angularly arranged around a longitudinal axis LA3 of thecontrol piston receiver 4206 whereby thestator 4200 is generally circularly shaped and symmetrical with respect to the longitudinal axis LA3. A center manifold engagement face 4213 (FIG. 55 ) of each one of thestator extensions 4204 is substantially flat and extends substantially perpendicular to the longitudinal axis LA3. - In some embodiments, the
control piston receiver 4206 includes areceiver neck 4214, areceiver end face 4216, and a controlpiston engaging member 4218. The controlpiston engaging member 4218 is generally a cylindrically shaped tubular body having anexterior surface 4222 and aninterior surface 4224. Theinterior surface 4224 defines acentral bore 4225 of the controlpiston engaging member 4216, which receives themain shaft 1000. A circumferential seal groove 4227 (FIGS. 46 and 56-58) can be provided in theinterior surface 4224 for receiving a seal (not shown) that engages a mating surface of themain shaft 1000. A controlpiston receiving chamber 4220 is defined between thereceiver neck 4214, thereceiver end face 4216, and the controlpiston engaging member 4218. Theexterior surface 4222 of the controlpiston engaging member 4218 and aninterior surface 4226 of thereceiver neck 4214 extend substantially parallel to each other and serve as control piston support surfaces. The controlpiston receiving chamber 4220 is configured for receiving one of the control pistons 2208 (FIG. 36-38 ). Theexterior surface 4222 of the controlpiston engaging member 4218 is configured (for example, has a sufficient smoothness and straightness) for forming a sealed interface with theinner seal 2214 of thecontrol piston 2208, and theinterior surface 4226 of thereceiver neck 4214 is configured for forming a sealed interface with theouter seal 2216 of thecontrol piston 2208. A longitudinal axis of the controlpiston engaging member 4218 extends coincidentally with the longitudinal axis LA3 of thecontrol piston receiver 4206. Thesurfaces - As best shown in
FIGS. 54 and 55 , a skewroller reaction surface 4228 and a shift guideroller reaction surface 4230 are provided at opposing edges of each shiftlever guide flange 4202. The skewroller reaction surface 4228 is substantially flat and the shift guideroller reaction surface 4230 is contoured. Examples of such contour include, but are not limited to, semi-circular, parabolic, elliptical and angularly tapered. In one embodiment, the contour is circular and the center of its radius of curvature is coincident with the center of tilt of theplanet 2102. Adjacent skew roller reaction surfaces 4228 of adjacent shiftlever guide flanges 4202 extend substantially parallel to each other and adjacent shift guide roller reaction surfaces 4230 of adjacent shiftlever guide flanges 4202 are substantially aligned. - As shown in
FIGS. 54-57 , in one embodiment, a control fluid communicatingbolt hole 4232 can be provided in one of thestator extensions 4204. In addition to serving as a bolt hole for receiving a bolt that secures thestator 4200 to the center manifold 4000 (that is, a stator securing bolt), the control fluid communicatingbolt hole 4232 can be configured to serve as a channel for fluid communication with the controlpiston receiving chamber 4220. In some embodiments, a lubricant communicatingbolt hole 4234 can be provided in a number ofother stator extensions 4204. In addition to serving as a bolt hole for receiving a bolt that secures thestator 4200 to thecenter manifold 4000, the lubricant communicatingbolt hole 4234 can be configured to serve as a channel for providing lubricant to a planet/shiftlever lubricant jet 4236 in thestator extension 4204, to an oilgalley feeding port 4238 in thereceiver neck 4214, and/or an output load cam assembly bearinglubricant jet 4240 in thereceiver end face 4216. - As best shown in
FIG. 56 , in one embodiment, the control fluid communicatingbolt hole 4232 has a stepped profile such that a first portion of the control fluid communicatingbolt hole 4232, which is exposed at thesecond side face 4212 of the respective shiftlever guide flange 4202, has a relatively close clearance fit with the stator securing bolt and a second portion of the control fluid communicatingbolt hole 4232, which is exposed at the centermanifold engagement face 4213 of thestator extension 4204, has an oversize clearance fit with the stator securing bolt. In this manner, the flow of control fluid past the stator securing bolt in the second portion of the control fluid communicatingbolt hole 4232 is essentially unrestricted. Drill holes 4242 that extend between the second portion of the control fluid communicatingbolt hole 4232 and the controlpiston receiving chamber 4220 in an intersecting manner form a control fluid channel between the control fluid communicatingbolt hole 4232 and the controlpiston receiving chamber 4220. The openings of the drill holes 4242 exposed at theextension 4204, exterior surface of thereceiver neck 4214, and at the exterior surface of thereceiver end face 4216 are plugged to prevent control fluid discharge therefrom. - In some embodiments, a lubricant communicating
bolt hole 4234 has a stepped profile such that a first portion of the lubricant communicatingbolt hole 4234, which is exposed at thesecond side face 4212 of the respective shiftlever guide flange 4202, has a relatively close clearance fit with the stator securing bolt and a second portion of the lubricant communicatingbolt hole 4234, which is exposed at the centermanifold engagement face 4213 of thestator extension 4204, has an oversize clearance fit with the stator securing bolt. In this manner, the lubricant flow past the stator securing bolt in the second portion of the lubricant communicatingbolt hole 4234 is essentially unrestricted. Drill holes 4244 that extend in an intersecting manner between the second portion of the lubricant communicatingbolt hole 4234 and the oilgalley feeding port 4238, and/or the bearinglubricant jet 4240, form a lubricant channel between the lubricant communicatingbolt hole 4234 and such ports and/or jets. The opening of the drill holes 4244 exposed at an exterior surface of thestator extensions 4204 can be plugged to prevent unintentional and/or undesirable lubricant discharge therefrom. For example, if thestator 4200 does not provide the output loadcam bearing assembly 2022B (FIG. 20 ) with a dedicated supply of lubricant, the drill hole forming the output load cam assembly bearinglubricant jet 4240 is plugged. - In one embodiment, a drill hole 4246 (
FIGS. 55 , 57 and 59) extending through one of the shiftlever guide flanges 4202 and thereceiver neck 4214 forms a passage that can be used for routing wires and/or housing a sensor (not shown) such as, for example, a proximity sensor which cooperates with acontoured recess 2242 of thecontrol piston 2208 for allowing a determination of the axial position of thecontrol piston 2208. Thedrill hole 4246 can be drilled from the outer diameter of the shiftlever guide flange 4202 through thereceiver neck 4214 into the controlpiston receiving chamber 4220. Similarly, aset screw hole 4248 can be formed in the receiver neck 4214 (for example, through one of the shift lever guide flanges 4202) for receiving an anti-rotation member (not shown) such as, for example, a set screw. The anti-rotation member cooperates with the groove 2246 (FIG. 38 ) of arespective control piston 2208 for precluding rotation of therespective control piston 2208 within the controlpiston receiving chamber 4220. - As shown in
FIG. 55 , thestator 4200 can includedowel pin holes 4250 for facilitating proper positioning of thestator 4200 with thecenter manifold 4000. In one embodiment, thedowel pin holes 4250 are located radially in line with the respective lubricant communicatingbolt hole 4234 of thestator 4200. The radial position of eachdowel pin hole 4250 is substantially the same as the radial position of each dowel pin hole 4305 of thecenter manifold 4000. Accordingly, dowel pins (not shown) of suitable length engaged with thedowel pin holes 4035 are coupled with corresponding dowel pin holes 4250, thereby facilitating proper alignment of thestator 4200 with thecenter manifold 4000. Furthermore, such a dowel pin hole arrangement enables positioning of thestator 4200 for aligning the control fluid communicatingbolt hole 4232 of thestator 4200 with either one of thecontrol fluid ports base plate 4015 or with either one of thecontrol fluid ports cover plate 4020, depending on which one of theplates stator 4200 is engaged with. In this manner, for example, thefirst stator 4200A aligns with the firstcontrol fluid port 4091 of thebase plate 4015, and thesecond stator 4200B aligns with the secondcontrol fluid port 4093 of thecover plate 4020, thereby allowing for communication of control fluid with thestators - Referring back to
FIGS. 45-47 and 51-54, in one embodiment, thefirst stator 4200A engages thefirst side face 4005 of the center manifold 4000 (FIGS. 45 and 46 ), and thesecond stator 4200B engages thesecond side face 4010 of thecenter manifold 4000. More specifically, the center manifold engagement face 4213 (FIG. 55 ) of eachstator extension 4204 of thefirst stator 4200A engages thefirst side face 4016A (FIGS. 46 and 49 ) of thebase plate 4015, and the centermanifold engagement face 4213 of eachstator extension 4204 of thesecond stator 4200B engages thesecond side face 4021B (FIGS. 48 and 53 ) of thecover plate 4020. Thefirst stator 4200A is placed such that the control fluid communicating bolt hole 4232 (FIGS. 54 and 55 ) of thefirst stator 4200A aligns with the first control fluid passage 4091 (FIG. 47 ) of thebase plate 4015 and thelubricant distribution channel 4085 of thecover plate 4020 aligns with thelubricant port 4087 of thebase plate 4015. In some embodiments, thesecond stator 4200B can be placed such that control fluid communicating bolt hole 4232 (FIGS. 53 and 54 ) of thesecond stator 4200B aligns with the second control fluid port 4094 (FIG. 47 ) of thecover plate 4020 and thelubricant communicating ports 4234 of thesecond stator 4200B align with thelubricant ports 4087 of thecover plate 4020. In this manner, control fluid can be communicated to and from the controlpiston receiving chamber 4220 of thefirst stator 4200A independently of control fluid communicated to and from the controlpiston receiving chamber 4220 of thesecond stator 4200B, and lubricant can be delivered to various ports and jets of thestators oil galleys - As shown in
FIGS. 44-46 , theoil galleys oil galley 4400. Referring now toFIGS. 60-62 , in one embodiment, theoil galley 4400 is generally circular and includes acentral bore 4402, anannular lubricant channel 4404, a number oflubricant jet channels 4406, and lubricant flow passages 4408 (for example, a drill hole). Thelubricant jet ports 4406 can be arranged in groupings (for example, linear, cluster, etc.) that are preferably, but not necessarily, spaced (example, uniformly) around thecentral bore 4402. Each group oflubricant jet ports 4406 can be in fluid communication with theannular lubricant channel 4404 by the respectivelubricant flow passage 4408. Theoil galley 4400 includes statorbolt clearance cutouts 4410 configured to allow access to bolts engaged within the bolt holes 4232, 4234 of the stators 4200 (FIGS. 45 and 46 ) that secure thestators 4200 to thecenter manifold 2300. - In some embodiments, the
central bore 4402 can be configured to engage the exterior surface of the receiver neck 4214 (FIGS. 45 and 46 ) of arespective stator 4200 by, for example, a press fit interface. Theoil galley 4400 can be positioned on thereceiver neck 4214 such that theannular lubricant channel 4404 aligns with the oil galley feeding port 4238 (FIG. 56 ) of thestator 4200, thereby facilitating supplying lubricant from thestator 4200 to theoil galley 4400. In one embodiment, theoil galley 4400 is angularly oriented such that each one of the groupings of thelubrication jet channels 4406 is aligned with a respective planet axle passage 4208 (FIGS. 45 and 54 ) of therespective stator 4200. Accordingly, when lubricant is supplied to theoil galley 4400 from therespective stator planet axle passage 4208 for lubricating components of an associated planet-and-shift-lever subassembly 2100. - Referring back to
FIGS. 45 and 46 , in one embodiment, thestators center manifold 4000 are securely coupled in aligned orientation using a fastening structure such as, for example, a bolt and nut (not shown). For example, an elongated portion of a threaded fastening structure (such as the shank of the bolt) extends through the bolt holes 4232, 4234 of thestators lubricant ports center manifold plates stators 4200 and thecenter manifold 4000 to form a substantially rigid support structure for components and subassemblies to be mounted thereon. In some embodiments, sealing washers are used under the bolt head and nut to seal the lubrication and control fluid passages. - Passing to
FIGS. 63 and 64 now, certain structure and functionality of thevariator 1200 will be discussed. In some embodiments, afirst control piston 2208A (FIG. 63 ) of the shift-cam-and-sun subassembly 2200 is slidably mounted within the control piston receiving chamber 4220 (seeFIGS. 56 and 57 ) of thefirst stator 4200A, and asecond control piston 2208B (FIG. 63 ) of the shift-cam-and-sun subassembly 2200 is slidably mounted within the controlpiston receiving chamber 4220 thesecond stator 4200B. Through the selective control of control fluid volume within the controlpiston receiving chambers 4220, the shift-cam-and-sun subassembly 2200 can be selectively and controllably displaced along the longitudinal axis LA1 of themain shaft 1000. As discussed above, in on embodiment, thecontrol pistons - Simultaneous engagement of each planet 2102 (one shown in
FIG. 63 ) with theinput traction ring 2010A, theoutput traction ring 2010B, and thesun 2202 constrains axially and radially theplanet 2102 of each planet-and-shift-lever subassembly 2100. Theplanet 2102 is rotatably mounted on therespective planet axle 2104. The skew roller 2122 (FIG. 63 ) of a planet-and-shift-lever subassembly 2100 engages skew roller reaction surfaces 4228 of adjacent shiftlever guide flanges 4202 positioned within a respectiveplanet axle passage 4208, thereby substantially precluding rotation of the respective planet-and-shift-lever subassembly 2100 about any radial axis extending perpendicular to the longitudinal axis LA1. The twoshift guide rollers 2114 of eachshift lever 2106 engage respective shift guide roller reaction surfaces 4230. Accordingly, a first one of theshift guide rollers 2114 engages a shift guideroller reaction surface 4230 on a first side of the respectiveplanet axle passage 4208, and a second one of theshift guide rollers 2114 engages a shift guideroller reaction surface 4230 on a second side of the respectiveplanet axle passage 4208. The semi-circular shape of the shift guide roller reaction surfaces 4230 and the corresponding engagement by theshift guide rollers 2114 serves to, among other things, substantially preclude axial displacement of the respective planet-and-shift-lever subassemblies 2100 with respect to relative to the longitudinal axis LA1, as well as to reduce the force needed to effect a tilting of theplanet axles 2104. It should be noted that the shift guide roller reaction surfaces 4230 cooperate with theshift guide rollers 2114 to react the shift forces that arise by the actuation of the planet-and-shift-lever subassemblies 2100 by the shift-cam-and-sun subassembly 2200. - Hence, in some embodiments, each planet-and-shift-
lever subassembly 2100 is substantially axially and radially constrained relative to the longitudinal axis LA1, and constrained with respect to rotation about any radial axis extending perpendicular to the longitudinal axis LA1. Conversely, each planet-and-shift-lever subassembly 2100 is pivotable about the respective tangential reference axis TA1, which extends through a center point of therespective planet 2102 substantially perpendicular to a radial reference axis extending from the longitudinal axis LA1 through the center point of therespective planet 2102. In some embodiments, theplanet 2102 is configured to freely move axially along the axis LA2 to allow for dimensional tolerances stack up between the traction components and the shift reaction surfaces. Additionally, the center of rotation of theplanet axle 2104 is not necessarily coincident with the center of rotation of theplanet 2102; such configuration prevents, in some cases, efficiency losses, increased shift forces, or outright binding of thevariator 1200. - In some embodiments, the
shift cam roller 2128 of eachshift lever 2106 couples to a cam surface of arespective shift cam 2206. A differential control fluid pressure between the controlpiston receiving chambers 4220 causes an axial translation of the shift-cam-and-sun subassembly 2200 along the axis LA1. Such axial translation results in force being exerted on theshift cam rollers 2128 coupled to theshift cam 2206 facing the direction of movement, thereby causing the planet-and-shift-lever subassemblies 2100 to synchronously pivot about the respective tangential reference axis TA1. The application of the same control fluid pressure within the controlpiston receiving chambers 4220 serves to hold the shift-cam-and-sun subassembly 2200 in a given position due to equal and opposing reactive forces being applied by theshift cams 2206 on the respectiveshift cam roller 2128. Thus, adjustment of the speed ratio of thevariator 1200 is facilitated through axial translation of the shift-cam-and-sun subassembly 2200 along the longitudinal axis LA1. - Various detailed aspects of the
torque converter subassembly 800 and thebell housing 1810 discussed above in reference toFIGS. 3A and 3B are shown inFIGS. 65-67 . In one embodiment, thebell housing 1810 includes a primemover mounting portion 1812 and a rearhousing mounting portion 1814. The primemover mounting portion 1812 can be configured for attachment to a structural portion of the prime mover (for example, a engine block, motor casing, etc.), and the rearhousing mounting portion 1814 can be configured for attachment to therear housing 1820 of the transmission housing 1800 (FIG. 3A ). As previously discussed, thetorque converter subassembly 800 is an embodiment of an input interface, which is suitably configured for implementation between a prime mover (not shown) and thevariator 1200. - In some embodiments, the
torque converter subassembly 800 can include aflex plate assembly 802, a torque converter 804 (FIGS. 66 and 67 ), and a transmission fluid pump 806 (FIGS. 66 and 67 ). Theflex plate assembly 802 includes aflex plate 803 andstarter gear ring 807 for enabling a rotary apparatus (for example, a starter motor) to turn moving components of the prime mover such as for starting the prime mover. Theflex plate 803 is configured for attachment to a power output portion (for example, a crankshaft or motor shaft) of the prime mover in a manner that precludes relative rotation of theflex plate 803 with respect to the power output portion of the prime mover, thereby enabling torque transfer from the prime mover to theflex plate 803. For example, theflex plate 803 typically connects to the prime mover with threaded fasteners (such as bolts). - In one embodiment, the
torque converter 804 includes a converter torque output portion 805 (FIG. 66 ), atorque converter housing 808, and various torque converting components (not shown) within thetorque converter housing 808 that enable torque converter fluid within thetorque converter housing 808 to be conveyed within thehousing 808 in a manner that transfers torque applied to thetorque converter housing 808 to the torqueconverter output portion 805. In some embodiments, the torqueconverter output portion 805 includes a turbine and a splined hub that fixedly attach to the turbine. The splined hub mates with the splines of the first end portion 1005 (FIGS. 3A , 4 and 5) of themain shaft 1000. Thetorque converter housing 808 is configured for attachment to theflex plate 803 in a manner that substantially precludes relative rotation of thetorque converter housing 808 with respect to theflex plate 803, thereby facilitating torque transfer from theflex plate 803 to thetorque converter housing 808. Examples of such ways for attaching thetorque converter housing 808 to theflex plate 803 include, but are not limited to, threaded fastener structures, pins, and the like. - The
transmission fluid pump 806 includes apump housing 812, atorque input shaft 814, and various fluid pumping components within the pump housing that facilitate application of torque to thetorque input shaft 814 to cause transmission fluid to be drawn into thepump housing 812 via a fluid supply input (not shown) and supplied from within thepump housing 812 under pressure via a fluid outlet (not shown). Thepump housing 812 fixedly attaches to apump mounting structure 815 of thebell housing 1820. Thetorque input shaft 814 attaches to thetorque converter housing 808 in a manner that substantially precludes relative rotation of thetorque input shaft 814 with respect to thetorque converter housing 808, thereby facilitating torque transfer from thetorque converter housing 808 to thetorque input shaft 814. - Various aspects of one embodiment of the combining
device 1400 discussed above in reference toFIGS. 3A and 3B are shown inFIGS. 68-71 . The combiningdevice 1400 can be an output interface, which is suitably configured for implementation between themain shaft 1000, thevariator 1200, and therangebox 1600. More specifically, themain shaft 1000 and thevariator 1200 supply power to the firstpower input portion 1405 and the secondpower input portion 1410, respectively, of the combiningdevice 1400, and thepower output portion 1422 of the combiningdevice 1400 supplies power to therangebox 1600. - Referring to
FIGS. 68-71 , in some embodiments, the combiningdevice 1400 can include ahub 1416, a plurality ofplanet gears 1418, a plurality ofplanet gear axles 1419, aplanet gear carrier 1420, a power output portion (or a transfer shaft) 1422, aneedle bearing 1424, aforward disk 1426, arear disk 1428, asun gear 1430, and athrust ring 1432. The planet gears 1418 are each rotatably mounted on theplanet gear carrier 1420 via one of the planet gear axles 1419 (FIG. 71 ). Eachplanet gear 1418 is positioned within a pocket region of theplanet gear carrier 1420 and the respectiveplanet gear axle 1419 is engaged within respective planet gear axle bores 1421 of theplanet gear carrier 1420. Thesun gear 1430 is positioned within the pocket region of theplanet gear carrier 1420, and the teeth of thesun gear 1430 are configured to engage the teeth of the planet gears 1418. In one embodiment, thesun gear 1430 includes a central bore havinginternal splines 1431, which are configured to engage splines at thesecond end portion 1015 of themain shaft 1000. - In one embodiment, the
transfer shaft 1422 includessplines splines 1434 engage mating splines of anextension portion 1442 of theplanet gear carrier 1420. In one embodiment, theneedle bearing 1424 is mounted within a pocket of thetransfer shaft 1422. As shown inFIG. 3A , a tip of themain shaft 1000 engages theneedle bearing 1424, thereby providing an aligned and supported interface therebetween. As is discussed below with reference toFIGS. 73 and 74 , thesplines rangebox 1600. - As best shown in
FIGS. 70 and 71 , therear disk 1428 can be configured to engage teeth adjacent arear edge 1444 of thehub 1416, thereby precluding relative rotation of therear disk 1428 with respect to thehub 1416. Theplanet gear carrier 1420 is positioned within thehub 1416 with a rear face of theplanet gear carrier 1420 abutting therear disk 1428. The teeth of the planet gears 1418 engage mating interior teeth of thehub 1416. In this manner, the secondpower input portion 1410 of the combiningdevice 1400 includes thehub 1416. Thethrust ring 1432 is positioned within thehub 1416, abutting a front face of theplanet gear carrier 1420. Theforward disk 1426 engages internal splines formed on afront edge 1446 of thehub 1416, thereby precluding relative rotation of theforward disk 1426 with respect to thehub 1416. Thus, theforward disk 1426 and therear disk 1428 axially constrain theplanet gear carrier 1420, reacting axial thrust in either direction from thesun gear 1430. A firstcircumferential groove 1448 and a secondcircumferential groove 1450 are provided adjacent thefront edge 1446 and therear edge 1444, respectively, and are each configured for respectively receiving a retention device such as, for example, a respective snap ring engaged therein for axially constraining thedisks FIGS. 69-71 ,exterior splines 1435 can be provided at thefront edge 1446 of thehub 1416. The exterior splines 1435 are configured for coupling to splines of theoutput load cam 2005B, for example. In this manner, the combiningdevice 1400 is configured for facilitating power transfer from thevariator 1200 to thecoupling device 1400. - Various aspects of the interoperability of the
variator 1200 and therangebox 1600 discussed above in reference toFIGS. 3-4 are shown inFIG. 72 . In some embodiments, themain shaft 1000 can be coupled directly to the input load-cam-and-traction-ring subassembly 2000A and to a firstpower input portion 1405 of the combiningdevice 1400. Each of the planets 2102 (one shown) is engaged between the input load-cam-and-traction-ring subassembly 2000A, the output load-cam-and-traction-ring subassembly 2000B, and thesun 2202. With respect to the input load-cam-and-traction-ring subassembly 2000A, theinput load cam 2005A couples to theinput traction ring 2010A through the inputload cam rollers 2015A. With respect to the output load-cam-and-traction-ring subassembly 2000B, theoutput load cam 2005B couples to theoutput traction ring 2010B through the outputload cam rollers 2015B. Theoutput load cam 2005B couples to the secondpower input portion 1410 of the combiningdevice 1400. - In one embodiment, the
transfer shaft 1422 of the combiningdevice 1400 couples to a direct clutch 1604 and to asun gear 1606 of a firstplanetary gearset 1608 of therangebox 1600. The firstplanetary gearset 1608 is supported on acarrier 1609. Asun gear 1610 of a secondplanetary gearset 1612 is configured for being selectively coupled to thetransfer shaft 1422 through the direct clutch 1604 or to thetransmission housing 1800. Thesun gear 1610 couples to thetransmission housing 1800 through either a forward clutch 1614, via an overrun clutch 1616 (for example, a one-way mechanical diode), or a low clutch 1618. Thesun gear 1610 couples to the firstplanetary gearset 1608. Aring gear 1622 couples to the first and secondplanetary gearsets reverse clutch 1624 of therangebox 1600. Anoutput shaft 1626 couples to thecarrier 1609. Preferably, but not necessarily, theoutput shaft 1626 and thecarrier 1609 are one integral part. - In accordance with one embodiment, the
rangebox 1600 is provided in a vehicle having an engine supplying power to thetransmission 600. Therangebox 1600 is controlled in conjunction with thevariator 1200 for providing thetransmission 600 with multiple modes of operation, in which the shifting control of thevariator 1200 is based on engine speed, vehicle speed, and/or user commands. A first power train operating mode (for example, Mode 1) refers to therangebox 1600 being engaged in a low gear range. A second power train operating mode (for example, Mode 2) refers to therangebox 1600 being engaged in a high gear range with thevariator 1200 in overdrive (that is, speed output from the range box is greater than speed input to the range box). - Operationally, for a vehicle acceleration event from a standing start (meaning, operating in Mode 1), as the engine initially increases speed, the
variator 1200 is maintained in an underdrive condition until the engine reaches a predetermined engine speed set point such as, for example, 1800 revolutions-per-minute (rpm). Once the predetermined engine speed set point is achieved, the engine speed is held constant while thevariator 1200 shifts its torque ratio in a manner that causes the vehicle speed to increase. Vehicle speed continues to increase until thevariator 1200 reaches a torque ratio corresponding to maximum overdrive, at which point, the engine speed increases up to a predetermined maximum engine speed (for example, maximum recommended engine rpm, peak horsepower, etc.). Once the engine speed reaches the maximum set point engine speed, therangebox 1600 is shifted fromMode 1 to Mode 2, with thevariator 1200 in overdrive. Following therangebox 1600 being shifted to Mode 2, the engine speed is initially decreased to cause synchronization between vehicle speed and engine speed. The engine can then be controlled to increase speed further by increasing engine speed with the variator in overdrive. - In one embodiment, one or more data processing units are programmed for facilitating the operating modes discussed above. A power train controller, an engine controller, and/or a transmission controller are examples of data processing units, which can be programmed for providing the operating modes discussed above. Various sensors and control devices are connected to the engine and/or
transmission 600 for facilitating the implementation of such modes of operation. In some embodiments, a hydraulic control structure having valving, among other things, can be used to convert electronic control algorithms to hydraulic and mechanical actuation of thevariator 1200 and/orrangebox 1600. - Referring now to
FIGS. 73 and 74 , on embodiment of therangebox 1600 discussed above in reference toFIGS. 3A , 3B and 72 is provided. Therangebox 1600 can include anintermediate support 1640, a high andlow mode subassembly 1642, and areverse mode subassembly 1644. - Various aspects of the
rear housing 1820 of thetransmission housing 1800 discussed above in reference toFIGS. 3A and 3B are shown inFIGS. 75-77 . In one embodiment, a bellhousing attachment portion 1816 of therear housing 1820 is configured for attachment to the rearhousing mounting portion 1814 of thebell housing 1810. A tailhousing attachment portion 1818 of therear housing 1820 is configured for attachment with a tail housing (not shown) of thetransmission 600 or to a housing of a related drivetrain subassembly. - In some embodiments, the
rear housing 1820 includes anaccess port 1822 configured for receiving and supporting a sensor (not shown) for monitoring speed of theinput load cam 2005A. Anaccess port 1824 is configured for receiving and supporting a sensor for monitoring speed of theoutput load cam 2005B.Passages 1826 are configured for receiving and supporting the cam dowels 4055 discussed above in reference toFIGS. 45-51 . In one embodiment, eachpassage 1826 is at least partially threaded for receiving a threaded fastener (for example, a setscrew) used for exerting a retention force on therespective cam dowel 4055. Asupport flange 1828 is provided within an interior space of therear housing 1820 for locating and axially supporting thecenter manifold 4000 through engagement with thelocating pads 4045 discussed above in reference toFIGS. 45-51 . A center manifoldfooting engagement shoulder 1830 is provided for engaging thefooting 4040 of thecenter manifold 4000. Threaded holes 1831 (one shown) are provided in the center manifoldfooting engagement shoulder 1830 for attaching thefooting 4040 to the center manifoldfooting engagement shoulder 1830. In one embodiment, to facilitate accurate positioning of the center manifold 2305, while at the same time avoiding the need for a close tolerance along the body of therear housing 1820, alocating diameter 1832 is provided within the interior space of therear housing 1820. A series ofclutch splines 1834 andgrooves 1836 are formed in interior wall surfaces of therear housing 1800 and are configured for receiving and supporting various components and/or assemblies of the rangebox 1600 (for example, clutches, gears, gearsets, snap rings, etc.). - In some embodiments, various ports are provided in a
bottom wall 1838 of therear housing 1820.Lubricant ports 1842 can be configured for communicating lubricant to thelubricant inlet ports 4076 of thebase plate 4015 of the center manifold 4000 (FIG. 50 ). First and secondcontrol fluid ports fluid inlet ports FIG. 50 ). A group ofancillary ports 1848 can be provided for facilitating selective and independent communication of other desired fluids with transmission components such as, for example, an external fluid cooler, an external fluid pump, etc., and/or for facilitating the mounting of one or more sensors (for example, a lubricant temperature sensor, a lubricant level sensor, etc.).
Claims (27)
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PCT/US2008/053347 WO2008100792A1 (en) | 2007-02-12 | 2008-02-07 | Continuously variable transmissions and methods therefor |
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US13/928,779 Expired - Fee Related US9371894B2 (en) | 2007-02-12 | 2013-06-27 | Continuously variable transmissions and methods therefor |
US15/186,898 Active 2029-05-15 US10260607B2 (en) | 2007-02-12 | 2016-06-20 | Continuously variable transmissions and methods therefor |
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US15/186,898 Active 2029-05-15 US10260607B2 (en) | 2007-02-12 | 2016-06-20 | Continuously variable transmissions and methods therefor |
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CN (2) | CN104121345B (en) |
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Cited By (66)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070155580A1 (en) * | 2005-12-09 | 2007-07-05 | Nichols Jon M | Continuously variable transmission |
US20080032854A1 (en) * | 2004-10-05 | 2008-02-07 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20090164076A1 (en) * | 2007-12-21 | 2009-06-25 | Fallbrook Technologies Inc. | Automatic transmissions and methods therefor |
US20090312145A1 (en) * | 2006-06-26 | 2009-12-17 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20100093480A1 (en) * | 2008-10-14 | 2010-04-15 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20100093476A1 (en) * | 2007-02-16 | 2010-04-15 | Fallbrook Technologies Inc. | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
US20100093485A1 (en) * | 2006-11-08 | 2010-04-15 | Fallbrook Technologies Inc. | Clamping force generator |
US20110034284A1 (en) * | 2005-12-30 | 2011-02-10 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7914029B2 (en) | 2005-11-22 | 2011-03-29 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20110105274A1 (en) * | 2008-06-06 | 2011-05-05 | Charles Lohr | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
US8066614B2 (en) * | 2003-02-28 | 2011-11-29 | Fallbrook Technologies, Inc. | Continuously variable transmission |
US8070635B2 (en) | 2005-10-28 | 2011-12-06 | Fallbrook Technologies Inc. | Electromotive drives |
US8087482B2 (en) | 2006-03-14 | 2012-01-03 | Fallbrook Technologies Inc. | Wheelchair |
US8313405B2 (en) | 2008-02-29 | 2012-11-20 | Fallbrook Intellectual Property Company Llc | Continuously and/or infinitely variable transmissions and methods therefor |
US8317651B2 (en) | 2008-05-07 | 2012-11-27 | Fallbrook Intellectual Property Company Llc | Assemblies and methods for clamping force generation |
CN102817984A (en) * | 2012-08-27 | 2012-12-12 | 北京理工大学 | Axial-loading biconical traction drive device |
US8360917B2 (en) | 2009-04-16 | 2013-01-29 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US8393989B2 (en) | 2007-04-24 | 2013-03-12 | Fallbrook Intellectual Property Company Llc | Electric traction drives |
US8398518B2 (en) | 2008-06-23 | 2013-03-19 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US8469856B2 (en) | 2008-08-26 | 2013-06-25 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US8512195B2 (en) | 2010-03-03 | 2013-08-20 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
US8641577B2 (en) | 2007-06-11 | 2014-02-04 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US8738255B2 (en) | 2007-02-01 | 2014-05-27 | Fallbrook Intellectual Property Company Llc | Systems and methods for control of transmission and/or prime mover |
US8776633B2 (en) | 2006-01-30 | 2014-07-15 | Fallbrook Intellectual Property Company Llc | System for manipulating a continuously variable transmission |
US20140228163A1 (en) * | 2011-09-22 | 2014-08-14 | Toyota Jidosha Kabushiki Kaisha | Continuously variable transmission apparatus |
US8818661B2 (en) | 2008-08-05 | 2014-08-26 | Fallbrook Intellectual Property Company Llc | Methods for control of transmission and prime mover |
US20140274535A1 (en) * | 2013-03-14 | 2014-09-18 | Team Industries, Inc. | Continuously variable transmission with differential controlling assemblies |
US8845485B2 (en) | 2011-04-04 | 2014-09-30 | Fallbrook Intellectual Property Company Llc | Auxiliary power unit having a continuously variable transmission |
WO2014179719A1 (en) * | 2013-05-03 | 2014-11-06 | Dana Limited | 4-mode rear wheel drive continuously variable planetary transmission |
US8888643B2 (en) | 2010-11-10 | 2014-11-18 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US8900085B2 (en) | 2007-07-05 | 2014-12-02 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US8926468B2 (en) | 2013-03-14 | 2015-01-06 | Dana Limited | Ball type continuously variable transmission |
US8986150B2 (en) | 2012-09-07 | 2015-03-24 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
US8996263B2 (en) | 2007-11-16 | 2015-03-31 | Fallbrook Intellectual Property Company Llc | Controller for variable transmission |
US9052000B2 (en) | 2012-09-07 | 2015-06-09 | Dana Limited | Ball type CVT/IVT including planetary gear sets |
US20150204430A1 (en) * | 2012-09-07 | 2015-07-23 | Dana Limited | Ball type cvt with powersplit paths |
JP2015527554A (en) * | 2012-09-07 | 2015-09-17 | デーナ リミテッド | Ball CVT including direct drive mode |
WO2016061500A1 (en) * | 2014-10-17 | 2016-04-21 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low part count |
US9347532B2 (en) | 2012-01-19 | 2016-05-24 | Dana Limited | Tilting ball variator continuously variable transmission torque vectoring device |
US9382988B2 (en) * | 2014-10-17 | 2016-07-05 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
US9404414B2 (en) | 2013-02-08 | 2016-08-02 | Dana Limited | Internal combustion engine coupled turbocharger with an infinitely variable transmission |
US9512911B2 (en) | 2014-10-17 | 2016-12-06 | Allison Transmission, Inc. | Split power continuously variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
US9541179B2 (en) | 2012-02-15 | 2017-01-10 | Dana Limited | Transmission and driveline having a tilting ball variator continuously variable transmission |
US9551404B2 (en) | 2013-03-14 | 2017-01-24 | Dana Limited | Continuously variable transmission and an infinitely variable transmission variator drive |
US9556941B2 (en) | 2012-09-06 | 2017-01-31 | Dana Limited | Transmission having a continuously or infinitely variable variator drive |
US9556943B2 (en) | 2012-09-07 | 2017-01-31 | Dana Limited | IVT based on a ball-type CVP including powersplit paths |
US9599204B2 (en) | 2012-09-07 | 2017-03-21 | Dana Limited | Ball type CVT with output coupled powerpaths |
US9611921B2 (en) | 2012-01-23 | 2017-04-04 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
US9644724B2 (en) | 2014-10-17 | 2017-05-09 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
US9644721B2 (en) | 2014-10-17 | 2017-05-09 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges and low variator load at vehicle launch |
US9677650B2 (en) | 2013-04-19 | 2017-06-13 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US9772017B2 (en) | 2014-10-17 | 2017-09-26 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low variator loading at vehicle launch |
US9777815B2 (en) | 2013-06-06 | 2017-10-03 | Dana Limited | 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission |
US9970521B1 (en) * | 2016-02-26 | 2018-05-15 | Rodney J. Cook and successors in trust | Infinitely variable transmission |
US10006529B2 (en) | 2014-06-17 | 2018-06-26 | Dana Limited | Off-highway continuously variable planetary-based multimode transmission including infinite variable transmission and direct continuously variable transmission |
US10030751B2 (en) | 2013-11-18 | 2018-07-24 | Dana Limited | Infinite variable transmission with planetary gear set |
US10030748B2 (en) | 2012-11-17 | 2018-07-24 | Dana Limited | Continuously variable transmission |
US10030594B2 (en) | 2015-09-18 | 2018-07-24 | Dana Limited | Abuse mode torque limiting control method for a ball-type continuously variable transmission |
US10047861B2 (en) | 2016-01-15 | 2018-08-14 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
US10088022B2 (en) | 2013-11-18 | 2018-10-02 | Dana Limited | Torque peak detection and control mechanism for a CVP |
US10260607B2 (en) | 2007-02-12 | 2019-04-16 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions and methods therefor |
US10458526B2 (en) | 2016-03-18 | 2019-10-29 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, systems and methods |
US10704662B2 (en) * | 2017-10-25 | 2020-07-07 | Zf Friedrichshafen Ag | Power-split continuously variable transmission device |
US11174922B2 (en) | 2019-02-26 | 2021-11-16 | Fallbrook Intellectual Property Company Llc | Reversible variable drives and systems and methods for control in forward and reverse directions |
US11215268B2 (en) | 2018-11-06 | 2022-01-04 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same |
US11667351B2 (en) | 2016-05-11 | 2023-06-06 | Fallbrook Intellectual Property Company Llc | Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmission |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11280394B2 (en) | 2009-03-30 | 2022-03-22 | Tq-Systems Gmbh | Gear, motor-gear unit, vehicle, generator with a gear, and force transmitting element |
US20140084588A1 (en) * | 2012-09-21 | 2014-03-27 | Giridhari L. Agrawal | Gas bearing supported turbomachine with reduction gear assembly |
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US9482328B2 (en) * | 2015-01-08 | 2016-11-01 | GM Global Technology Operations LLC | Multi-mode transmission for vehicle powertrain system |
US9688276B2 (en) | 2015-02-26 | 2017-06-27 | Caterpillar Inc. | System and method for controlling engine and transmission system of a machine |
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US9822870B2 (en) | 2015-04-03 | 2017-11-21 | Allison Transmission, Inc. | Manufacturing technique for variator cooling technologies |
WO2016164026A1 (en) * | 2015-04-09 | 2016-10-13 | Allison Transmission Inc. | Continuously variable planetary transmission |
US20170146111A1 (en) * | 2015-11-23 | 2017-05-25 | GM Global Technology Operations LLC | Bolt cover |
DE102016122845A1 (en) | 2016-11-28 | 2018-05-30 | Tq-Systems Gmbh | Harmonic pinion gear, torque measuring device and freewheel assembly |
DE102017215784A1 (en) * | 2017-09-07 | 2019-03-07 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
CN108725683A (en) * | 2018-06-29 | 2018-11-02 | 浙江超级电气科技有限公司 | A kind of intelligent electric wheel hub |
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Citations (85)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US575533A (en) * | 1897-01-19 | James philip ottaway | ||
US719595A (en) * | 1901-07-06 | 1903-02-03 | Jacob B Huss | Bicycle driving mechanism. |
US1175677A (en) * | 1914-10-24 | 1916-03-14 | Roderick Mcclure | Power-transmitting device. |
US1793571A (en) * | 1929-12-14 | 1931-02-24 | Frank O Vaughn | Variable-speed drive |
US1847027A (en) * | 1930-02-19 | 1932-02-23 | Thomsen Thomas Peter | Change-speed gear |
US1903228A (en) * | 1927-10-21 | 1933-03-28 | Gen Motors Corp | Frictional gearing |
US2030203A (en) * | 1934-05-31 | 1936-02-11 | Gen Motors Corp | Torque loading lash adjusting device for friction roller transmissions |
US2109845A (en) * | 1932-07-23 | 1938-03-01 | Erban Operating Corp | Power transmission mechanism |
US2112763A (en) * | 1933-12-28 | 1938-03-29 | Cloudsley John Leslie | Variable speed power transmission mechanism |
US2269434A (en) * | 1940-11-18 | 1942-01-13 | Cuyler W Brooks | Automatic transmission mechanism |
US2461258A (en) * | 1946-06-06 | 1949-02-08 | Cuyler W Brooks | Automatic transmission mechanism |
US2730904A (en) * | 1952-07-14 | 1956-01-17 | Rennerfelt Sven Bernhard | Continuously variable speed gears |
US2868038A (en) * | 1955-05-26 | 1959-01-13 | Liquid Controls Corp | Infinitely variable planetary transmission |
US2874592A (en) * | 1955-11-07 | 1959-02-24 | Mcculloch Motors Corp | Self-controlled variable speed planetary type drive |
US3487727A (en) * | 1966-11-30 | 1970-01-06 | Bror Artur Gustafsson | Continuously variable speed variators |
US3487726A (en) * | 1966-07-04 | 1970-01-06 | Self Changing Gears Ltd | Auxiliary overdrive gear |
US3707888A (en) * | 1970-07-31 | 1973-01-02 | Roller Gear Ltd | Variable speed transmission |
US3866985A (en) * | 1974-03-04 | 1975-02-18 | Caterpillar Tractor Co | Track roller |
US3934493A (en) * | 1973-12-15 | 1976-01-27 | Raleigh Industries Limited | Epicyclic change speed gears |
US4369667A (en) * | 1981-07-10 | 1983-01-25 | Vadetec Corporation | Traction surface cooling method and apparatus |
US4494524A (en) * | 1982-07-19 | 1985-01-22 | Lee Wagner | Centrifugal heating unit |
US4496051A (en) * | 1981-06-09 | 1985-01-29 | Ortner Georg J | Container with information-carrying element |
US4574649A (en) * | 1982-03-10 | 1986-03-11 | B. D. Yim | Propulsion and speed change mechanism for lever propelled bicycles |
US4651082A (en) * | 1985-04-03 | 1987-03-17 | Mitsubishi Denki Kabushiki Kaisha | Generating apparatus with an adjustable speed change mechanism |
US4900046A (en) * | 1987-10-06 | 1990-02-13 | Aranceta Angoitia Inaki | Transmission for bicycles |
US4909101A (en) * | 1988-05-18 | 1990-03-20 | Terry Sr Maurice C | Continuously variable transmission |
US5379661A (en) * | 1992-03-13 | 1995-01-10 | Nsk Ltd. | Loading cam device |
US5383677A (en) * | 1994-03-14 | 1995-01-24 | Thomas; Timothy N. | Bicycle body support apparatus |
US5387000A (en) * | 1992-07-22 | 1995-02-07 | Sato; Yasunori | Hydraulic drive system for bicycles and the like |
US5401221A (en) * | 1990-08-17 | 1995-03-28 | Torotrak (Development) Limited | Transmission of the toroidal-race, rolling-traction type having a mixer and a reducer epicyclic type gearing with clutches brakes |
US5489003A (en) * | 1992-05-29 | 1996-02-06 | Honda Giken Kogyo Kabushiki Kaisha | Electric vehicle |
US5564998A (en) * | 1993-01-18 | 1996-10-15 | Torotrak (Development) Limited | Continuously-variable-ratio-transmissions |
US5601301A (en) * | 1989-12-18 | 1997-02-11 | Liu; Qingshan | Drive system for muscle-powered equipment and vehicles, in particular bicycles |
US5607373A (en) * | 1994-04-28 | 1997-03-04 | Nissan Motor Co., Ltd. | CVT ratio rate control as a function of throttle release rate |
US5888160A (en) * | 1996-11-13 | 1999-03-30 | Nsk Ltd. | Continuously variable transmission |
US6019701A (en) * | 1997-03-07 | 2000-02-01 | Nissan Motor Co., Ltd. | Shift control apparatus for continuously variable transmission |
US6029990A (en) * | 1997-05-13 | 2000-02-29 | Gt Bicycles, Inc. | Direct drive bicycle |
US6042132A (en) * | 1995-03-13 | 2000-03-28 | Sakae Co., Ltd. | Bicycle and bicycle speed change operation assembly |
US6045477A (en) * | 1999-06-14 | 2000-04-04 | General Motors Corporation | Continuously variable multi-range powertrain with a geared neutral |
US6099431A (en) * | 1999-05-06 | 2000-08-08 | Ford Global Technologies, Inc. | Method for operating a traction drive automatic transmission for automotive vehicles |
US6171210B1 (en) * | 1997-08-12 | 2001-01-09 | Nsk Ltd. | Toroidal type continuous variable transmission system |
US6186922B1 (en) * | 1997-03-27 | 2001-02-13 | Synkinetics, Inc. | In-line transmission with counter-rotating outputs |
US6251038B1 (en) * | 1998-10-21 | 2001-06-26 | Nsk Ltd. | Continuously variable transmission unit |
US6258003B1 (en) * | 1999-02-15 | 2001-07-10 | Nissan Motor Co., Ltd. | Infinite speed ratio transmission device and assembly method thereof |
US20020019285A1 (en) * | 2000-08-11 | 2002-02-14 | Steffen Henzler | Transmission arrangement |
US20020028722A1 (en) * | 2000-07-21 | 2002-03-07 | Nissan Motor Co., Ltd. | Control of infinitely variable transmission |
US6358178B1 (en) * | 2000-07-07 | 2002-03-19 | General Motors Corporation | Planetary gearing for a geared neutral traction drive |
US20020045511A1 (en) * | 2000-05-05 | 2002-04-18 | Daimlerchrysler Ag. | Continuously variable vehicle transmission |
US6494805B2 (en) * | 2000-07-27 | 2002-12-17 | Honda Giken Kogyo Kabushiki Kaisha | Continuously variable transmission system for vehicle |
US20030022753A1 (en) * | 2001-07-26 | 2003-01-30 | Toyota Jidosha Kabushiki Kaisha | Control system and method for vehicle having continuously variable transmission |
US20030036456A1 (en) * | 2000-03-23 | 2003-02-20 | Alfred Skrabs | Method for assembling a planetary gear unit in a precise position |
US6532890B2 (en) * | 2001-06-14 | 2003-03-18 | Ad-Ii Engineering Inc. | Speed indicator for a shifting device of bicycle |
US20030216216A1 (en) * | 2002-04-18 | 2003-11-20 | Nsk Ltd. | Apparatus and method for controlling transmission ratio of toroidal-type continuously variable transmission unit for continuously variable transmission apparatus |
US6659901B2 (en) * | 2000-03-30 | 2003-12-09 | Nissan Motor Co., Ltd. | Infinite speed ratio continuously variable transmission |
US6672418B1 (en) * | 1998-06-29 | 2004-01-06 | Yamaha Hatsudoki Kabushiki Kaisha | Electric motor-assisted vehicle |
US6676559B2 (en) * | 1997-09-02 | 2004-01-13 | Motion Technologies, Llc | Continuously variable transmission |
US6679109B2 (en) * | 2000-11-30 | 2004-01-20 | Zf Batavia Llc | Acoustic recognition of variator slip of a continuously variable transmission |
US6682432B1 (en) * | 2002-09-04 | 2004-01-27 | Kinzou Shinozuka | Multiple shaft diameter flexible coupling system |
US6689012B2 (en) * | 2001-04-26 | 2004-02-10 | Motion Technologies, Llc | Continuously variable transmission |
US20040058772A1 (en) * | 2002-08-23 | 2004-03-25 | Nsk Ltd. | Toroidal-type continuously variable transmission and continuously variable transmission apparatus |
US6723016B2 (en) * | 2001-09-27 | 2004-04-20 | Jatco Ltd | Torque split infinitely variable transmission |
US20040082421A1 (en) * | 2002-10-24 | 2004-04-29 | Jurgen Wafzig | Split performance power train |
US6849020B2 (en) * | 2002-08-07 | 2005-02-01 | Jatco Ltd | Continuously variable power-split transmission |
US6932739B2 (en) * | 2001-12-25 | 2005-08-23 | Nsk Ltd. | Continuously variable transmission apparatus |
US6958029B2 (en) * | 2002-11-28 | 2005-10-25 | Nsk Ltd. | Continuously variable transmission apparatus |
US6991575B2 (en) * | 2003-02-14 | 2006-01-31 | Nsk Ltd | Continuously variable transmission apparatus |
US6991579B2 (en) * | 2001-10-19 | 2006-01-31 | Nsk Ltd. | Toroidal type continuously variable transmission |
US20060052204A1 (en) * | 2002-09-05 | 2006-03-09 | Harald Eckert | Electromagnetic selection device for a two-stage planetary gear set |
US7011601B2 (en) * | 1997-09-02 | 2006-03-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7011600B2 (en) * | 2003-02-28 | 2006-03-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7029418B2 (en) * | 2000-12-28 | 2006-04-18 | Toyota Jidosha Kabushiki Kaisha | Toroidal type continuoulsy variable transmission |
US7077777B2 (en) * | 2001-10-05 | 2006-07-18 | Nsk Ltd. | Continuously variable transmission |
US7094171B2 (en) * | 2002-12-05 | 2006-08-22 | Nsk Ltd. | Continuously variable transmission apparatus |
US20070004552A1 (en) * | 2005-06-30 | 2007-01-04 | Honda Motor Co., Ltd. | Continuously variable transmission controller |
US7160220B2 (en) * | 2003-07-14 | 2007-01-09 | Nsk Ltd. | Continuously variable transmission apparatus |
US7166052B2 (en) * | 2003-08-11 | 2007-01-23 | Fallbrook Technologies Inc. | Continuously variable planetary gear set |
US20070049450A1 (en) * | 2005-08-24 | 2007-03-01 | Miller Donald C | Continuously variable transmission |
US20070149342A1 (en) * | 2004-04-30 | 2007-06-28 | Ruehle Guenter | Toroidal transmission |
US7238139B2 (en) * | 2005-01-06 | 2007-07-03 | Ford Global Technologies, Inc. | Electric and hybrid electric powertrain for motor vehicles |
US20080032854A1 (en) * | 2004-10-05 | 2008-02-07 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080046403A1 (en) * | 2004-12-23 | 2008-02-21 | Microsoft Corporation | Easy-to-use data report specification |
US7591755B2 (en) * | 2004-05-11 | 2009-09-22 | Getrag Getriebe-Und Zahnradfabrik Hermann Hagenmeyer Gmbh | Hydraulic circuit for a toroidal transmission |
US20100056322A1 (en) * | 2008-08-26 | 2010-03-04 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20120043841A1 (en) * | 2005-10-28 | 2012-02-23 | Fallbrook Technologies Inc. | Electromotive drives |
US8142323B2 (en) * | 2005-03-31 | 2012-03-27 | Torotrak (Development) Limited | Continuously variable transmission |
Family Cites Families (606)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1121210A (en) | 1914-12-15 | Fried Krupp Germaniawerft Ag | Submarine boat. | |
GB592320A (en) | 1945-03-13 | 1947-09-15 | Frederick Whigham Mcconnel | Improvements in or relating to variable speed-gears |
US2675713A (en) | 1954-04-20 | Protective mechanism for variable | ||
USRE22761E (en) | 1946-05-28 | Transmission | ||
US1207985A (en) | 1914-08-17 | 1916-12-12 | Charles I Null | Antifriction-hanger. |
US1380006A (en) | 1917-08-04 | 1921-05-31 | Hamilton Beach Mfg Co | Variable-speed transmission |
JP3223241B2 (en) | 1997-03-17 | 2001-10-29 | 本田技研工業株式会社 | Belt type continuously variable transmission |
US1390971A (en) | 1921-01-24 | 1921-09-13 | Samain Pierre | Gearing |
US1558222A (en) | 1924-01-14 | 1925-10-20 | Beetow Albert | Backlash take-up for gears |
US1629902A (en) | 1924-08-07 | 1927-05-24 | Arter Jakob | Power-transmitting device |
CH118064A (en) | 1924-08-07 | 1926-12-16 | Jakob Arter | Friction change transmission. |
US1686446A (en) | 1926-04-15 | 1928-10-02 | John A Gilman | Planetary transmission mechanism |
FR620375A (en) | 1926-06-24 | 1927-04-21 | Automatic pressure device for friction plates | |
US1774254A (en) | 1927-06-28 | 1930-08-26 | John F Daukus | Clutch mechanism |
DE498701C (en) | 1927-11-18 | 1930-05-31 | Jakob Arter | Friction ball change gear |
US1865102A (en) | 1929-05-07 | 1932-06-28 | Frank A Hayes | Variable speed transmission mechanism |
US1978439A (en) | 1930-04-01 | 1934-10-30 | John S Sharpe | Variable transmission |
US1850189A (en) | 1930-07-16 | 1932-03-22 | Carl W Weiss | Transmission device |
GB391448A (en) | 1930-08-02 | 1933-04-27 | Frank Anderson Hayes | Improvements in or relating to friction transmission |
US1858696A (en) | 1931-07-08 | 1932-05-17 | Carl W Weiss | Transmission |
US2131158A (en) | 1932-02-03 | 1938-09-27 | Gen Motors Corp | Continuously variable transmission |
US2086491A (en) | 1932-04-11 | 1937-07-06 | Adiel Y Dodge | Variable speed transmission |
US2196064A (en) | 1933-02-04 | 1940-04-02 | Erban Patents Corp | Driving energy consumer |
US2060884A (en) | 1933-09-19 | 1936-11-17 | Erban Operating Corp | Power transmission mechanism |
US2134225A (en) | 1935-03-13 | 1938-10-25 | Christiansen Ejnar | Variable speed friction gear |
US2152796A (en) | 1935-03-13 | 1939-04-04 | Erban Patents Corp | Variable speed transmission |
US2100629A (en) | 1936-07-18 | 1937-11-30 | Chilton Roland | Transmission |
US2209254A (en) | 1938-07-29 | 1940-07-23 | Yrjo A Ahnger | Friction transmission device |
US2259933A (en) | 1939-02-20 | 1941-10-21 | John O Holloway | Clutch coupling for motor vehicles |
US2325502A (en) | 1940-03-08 | 1943-07-27 | Georges Auguste Felix | Speed varying device |
US2595367A (en) | 1943-11-09 | 1952-05-06 | Picanol Jaime | Toroidal variable-speed gear drive |
US2480968A (en) | 1944-08-30 | 1949-09-06 | Ronai Ernest | Variable transmission means |
US2469653A (en) | 1945-02-01 | 1949-05-10 | Kopp Jean | Stepless variable change-speed gear with roller bodies |
US2596538A (en) | 1946-07-24 | 1952-05-13 | Allen A Dicke | Power transmission |
US2553465A (en) | 1946-11-30 | 1951-05-15 | Monge Jean Raymond Barthelemy | Manual or power-operated planetary transmission |
BE488557A (en) | 1948-04-17 | |||
US2586725A (en) | 1950-02-08 | 1952-02-19 | Roller Gear Corp | Variable-speed transmission |
US2696888A (en) | 1951-05-26 | 1954-12-14 | Curtiss Wright Corp | Propeller having variable ratio transmission for changing its pitch |
US2716357A (en) | 1952-07-07 | 1955-08-30 | Rennerfelt Sven Bernhard | Continuously variable speed gears |
US2748614A (en) | 1953-06-23 | 1956-06-05 | Zenas V Weisel | Variable speed transmission |
US2901924A (en) | 1954-08-05 | 1959-09-01 | New Prod Corp | Accessory drive |
US2873911A (en) | 1955-05-26 | 1959-02-17 | Librascope Inc | Mechanical integrating apparatus |
US2913932A (en) | 1955-10-04 | 1959-11-24 | Mcculloch Motors Corp | Variable speed planetary type drive |
US2959063A (en) | 1956-09-11 | 1960-11-08 | Perbury Engineering Ltd | Infinitely variable change speed gears |
US2891213A (en) | 1956-10-30 | 1959-06-16 | Electric Control Corp | Constant frequency variable input speed alternator apparatuses |
US2931235A (en) | 1957-11-12 | 1960-04-05 | George Cohen 600 Group Ltd | Variable speed friction drive transmissions |
US2931234A (en) | 1957-11-12 | 1960-04-05 | George Cohen 600 Group Ltd | Variable speed friction drive trans-mission units |
US2883883A (en) | 1957-11-13 | 1959-04-28 | Curtiss Wright Corp | Variable speed transmission |
US2964959A (en) | 1957-12-06 | 1960-12-20 | Gen Motors Corp | Accessory drive transmission |
DE1171692B (en) | 1958-01-09 | 1964-06-04 | Fabrications Unicum Soc D | Friction gear with several flat friction discs |
BE574149A (en) | 1958-01-09 | 1959-04-16 | Fabrications Unicum Soc D | Pressure device of friction speed variators |
US3048056A (en) | 1958-04-10 | 1962-08-07 | Gen Motors Corp | Drive system |
US3035460A (en) | 1958-12-02 | 1962-05-22 | Guichard Louis | Automatic infinitely variablespeed drive |
US2959070A (en) | 1959-01-09 | 1960-11-08 | Borg Warner | Accessory drive |
US2959972A (en) | 1959-02-11 | 1960-11-15 | Avco Mfg Corp | Single ball joint roller support for toroidal variable ratio transmissions |
US3051020A (en) | 1959-02-16 | 1962-08-28 | Thornton Axle Inc | Locking differential with pressure relief device |
US3008061A (en) | 1959-04-21 | 1961-11-07 | Barden Corp | Slow speed motor |
US2949800A (en) | 1959-05-11 | 1960-08-23 | Neuschotz Robert | Tool for installing threaded elements |
US3248960A (en) | 1959-11-13 | 1966-05-03 | Roller Gear Ltd | Variable speed drive transmission |
DE1178259B (en) | 1959-12-03 | 1964-09-17 | Motoren Werke Mannheim Ag | Main and secondary connecting rod for V machines |
US3204476A (en) | 1960-04-05 | 1965-09-07 | William S Rouverol | Variable speed transmission |
US3237468A (en) | 1960-05-13 | 1966-03-01 | Roller Gear Ltd | Variable speed drive transmission |
US3246531A (en) | 1960-11-04 | 1966-04-19 | Kashihara Manabu | Infinitely variable speed change gear |
DE1217166B (en) | 1960-11-04 | 1966-05-18 | Manabu Kashihara | Ball friction gear with swiveling balls |
BE629125A (en) | 1961-03-08 | |||
US3229538A (en) | 1961-09-25 | 1966-01-18 | Roller Gear Ltd | Variable speed drive transmission |
US3154957A (en) | 1961-10-16 | 1964-11-03 | Kashihara Manabu | Infinitely variable speed change gear utilizing a ball |
US3086704A (en) | 1961-11-24 | 1963-04-23 | Ryan Aeronautical Co | Cosine-secant multiplier |
CH398236A (en) | 1962-09-20 | 1965-08-31 | Yamamoto Sota | Friction stepless speed variator |
US3216283A (en) | 1963-03-04 | 1965-11-09 | Ford Motor Co | Variable speed torque transmitting means |
US3283614A (en) | 1963-04-10 | 1966-11-08 | Gen Motors Corp | Friction drive mechanism |
US3163050A (en) | 1963-06-19 | 1964-12-29 | Excelermatic | Toroidal transmission bearing means |
US3211364A (en) | 1963-10-30 | 1965-10-12 | Lau Blower Co | Blower wheel |
US3184983A (en) | 1963-10-30 | 1965-05-25 | Excelermatic | Toroidal transmission mechanism with torque loading cam means |
FR1376401A (en) | 1963-12-05 | 1964-10-23 | Fabrications Unicum Soc D | Improvements to the adjustment device of friction speed variators in particular |
JPS441098Y1 (en) | 1964-12-24 | 1969-01-17 | ||
JPS422843Y1 (en) | 1965-01-18 | 1967-02-20 | ||
US3273468A (en) | 1965-01-26 | 1966-09-20 | Fawick Corp | Hydraulic system with regenerative position |
JPS422844Y1 (en) | 1965-02-06 | 1967-02-20 | ||
JPS413126Y1 (en) | 1965-08-04 | 1966-02-23 | ||
US3340895A (en) | 1965-08-27 | 1967-09-12 | Sanders Associates Inc | Modular pressure regulating and transfer valve |
GB1119988A (en) | 1965-10-14 | 1968-07-17 | Nat Res Dev | Transmission system for interconnecting two rotary machines |
US3464281A (en) | 1965-10-27 | 1969-09-02 | Hiroshi Azuma | Friction-type automatic variable speed means |
GB1132473A (en) | 1965-11-15 | 1968-11-06 | James Robert Young | Variable ratio friction transmission and control system therefor |
US3280646A (en) | 1966-02-02 | 1966-10-25 | Ford Motor Co | Control system for an infinitely variable speed friction drive |
JPS47448B1 (en) | 1966-07-08 | 1972-01-07 | ||
US3430504A (en) | 1966-08-29 | 1969-03-04 | Gen Motors Corp | Transmission |
GB1195205A (en) | 1966-09-12 | 1970-06-17 | Nat Res Dev | Improvements in or relating to Toroidal Race Transmission Units. |
US3407687A (en) | 1967-03-27 | 1968-10-29 | Hayashi Tadashi | Variable ratio power transmission device |
JPS47962Y1 (en) | 1967-05-09 | 1972-01-14 | ||
US3477315A (en) | 1967-12-18 | 1969-11-11 | Elmer Fred Macks | Dynamoelectric device with speed change mechanism |
JPS47448Y1 (en) | 1967-12-27 | 1972-01-10 | ||
JPS4720535Y1 (en) | 1968-06-14 | 1972-07-10 | ||
JPS47207Y1 (en) | 1968-06-24 | 1972-01-07 | ||
JPS4912742Y1 (en) | 1968-12-18 | 1974-03-28 | ||
JPS4729762Y1 (en) | 1969-03-03 | 1972-09-06 | ||
US3574289A (en) | 1969-05-06 | 1971-04-13 | Gen Motors Corp | Transmission and control system |
US3581587A (en) | 1969-05-06 | 1971-06-01 | Gen Motors Corp | Transmission |
BE732960A (en) | 1969-05-13 | 1969-10-16 | ||
JPS4912742B1 (en) | 1969-10-15 | 1974-03-27 | ||
JPS4941536B1 (en) | 1969-11-27 | 1974-11-09 | ||
NL7004605A (en) | 1970-04-01 | 1971-10-05 | ||
JPS4913823Y1 (en) | 1970-10-31 | 1974-04-05 | ||
US3695120A (en) | 1971-01-14 | 1972-10-03 | Georg Titt | Infinitely variable friction mechanism |
JPS5232351Y2 (en) | 1971-02-05 | 1977-07-23 | ||
CH534826A (en) | 1971-02-18 | 1973-03-15 | Zuercher Andre | Friction gear |
US3727473A (en) | 1971-04-14 | 1973-04-17 | E Bayer | Variable speed drive mechanisms |
JPS5235481Y2 (en) | 1971-05-13 | 1977-08-12 | ||
US3727474A (en) | 1971-10-04 | 1973-04-17 | Fullerton Transiission Co | Automotive transmission |
JPS5032867Y2 (en) | 1971-10-21 | 1975-09-25 | ||
JPS5125903B2 (en) | 1971-11-13 | 1976-08-03 | ||
US3768715A (en) | 1972-05-01 | 1973-10-30 | Bell & Howell Co | Planetary differential and speed servo |
JPS4941536U (en) | 1972-07-14 | 1974-04-12 | ||
JPS5348166Y2 (en) | 1972-07-29 | 1978-11-17 | ||
US3802284A (en) | 1972-08-02 | 1974-04-09 | Rotax Ltd | Variable-ratio toric drive with hydraulic relief means |
US3987681A (en) | 1972-08-09 | 1976-10-26 | Gulf & Western Industrial Products Company | Clamp for presses |
US3810398A (en) | 1972-11-16 | 1974-05-14 | Tracor | Toric transmission with hydraulic controls and roller damping means |
US3820416A (en) | 1973-01-05 | 1974-06-28 | Excelermatic | Variable ratio rotary motion transmitting device |
DE2310880A1 (en) | 1973-03-05 | 1974-09-12 | Helmut Koerner | RING ADJUSTMENT DEVICE FOR CONTINUOUSLY ADJUSTABLE BALL REVERSING GEAR |
IT1016679B (en) | 1973-07-30 | 1977-06-20 | Valdenaire J | TRANSMISSION DEVICE PARTS COLARLY FOR MOTOR VEHICLES |
GB1376057A (en) | 1973-08-01 | 1974-12-04 | Allspeeds Ltd | Steplessly variable friction transmission gears |
US4023442A (en) | 1973-08-16 | 1977-05-17 | Oklahoma State University | Automatic control means for infinitely variable transmission |
JPS5125903Y2 (en) | 1973-11-06 | 1976-07-01 | ||
JPS547337B2 (en) | 1974-02-27 | 1979-04-05 | ||
JPS5618748Y2 (en) | 1974-02-28 | 1981-05-01 | ||
GB1469776A (en) | 1974-03-05 | 1977-04-06 | Cam Gears Ltd | Speed control devices |
US3891235A (en) | 1974-07-02 | 1975-06-24 | Cordova James De | Bicycle wheel drive |
US3954282A (en) | 1974-07-15 | 1976-05-04 | Hege Advanced Systems Corporation | Variable speed reciprocating lever drive mechanism |
JPS51150380U (en) | 1975-05-26 | 1976-12-01 | ||
JPS51150380A (en) | 1975-06-18 | 1976-12-23 | Babcock Hitachi Kk | Response property variable ae sensor |
DE2532661C3 (en) | 1975-07-22 | 1978-03-09 | Jean Walterscheid Gmbh, 5204 Lohmar | Telescopic shaft, in particular for agricultural machinery |
JPS5916719B2 (en) | 1975-09-13 | 1984-04-17 | 松下電工株式会社 | discharge lamp starting device |
US4098146A (en) | 1976-09-10 | 1978-07-04 | Textron Inc. | Traction-drive transmission |
JPS5647231Y2 (en) | 1977-05-17 | 1981-11-05 | ||
US4177683A (en) | 1977-09-19 | 1979-12-11 | Darmo Corporation | Power transmission mechanism |
US4159653A (en) | 1977-10-05 | 1979-07-03 | General Motors Corporation | Torque-equalizing means |
US4169609A (en) | 1978-01-26 | 1979-10-02 | Zampedro George P | Bicycle wheel drive |
GB1600646A (en) | 1978-03-22 | 1981-10-21 | Olesen H T | Power transmission having a continuously variable gear ratio |
CA1115218A (en) | 1978-09-01 | 1981-12-29 | Yves J. Kemper | Hybrid power system and method for operating same |
US4314485A (en) | 1978-11-16 | 1982-02-09 | Cam Gears Limited | Speed control systems |
GB2035481B (en) | 1978-11-16 | 1983-01-19 | Cam Gears Ltd | Speed control systems |
CH632071A5 (en) | 1978-11-20 | 1982-09-15 | Beka St Aubin Sa | VARIATOR. |
US4227712A (en) | 1979-02-14 | 1980-10-14 | Timber Dick | Pedal driven vehicle |
JPS5834381Y2 (en) | 1979-03-20 | 1983-08-02 | 株式会社ガスタ− | Solar hot water heating storage device |
JPS55135259A (en) | 1979-04-05 | 1980-10-21 | Toyota Motor Corp | Cup-type stepless speed change gear |
FR2460427A1 (en) | 1979-06-29 | 1981-01-23 | Seux Jean | Speed variator with coaxial input and output shafts - has friction discs on intermediate spheres with variable axes retained by thrust washers |
JPS5624251A (en) | 1979-07-31 | 1981-03-07 | Mitsubishi Heavy Ind Ltd | Rolling transmission planetary roller device with combined clutch function |
JPS5647231A (en) | 1979-09-25 | 1981-04-28 | Komatsu Metsuku Kk | Forming method for fan blade of cooling fan |
JPS56101448A (en) | 1980-01-10 | 1981-08-14 | Nissan Motor Co Ltd | Frictional transmission device |
JPS56127852A (en) | 1980-03-12 | 1981-10-06 | Toyoda Mach Works Ltd | Stepless transmission device |
EP0043184B1 (en) | 1980-05-31 | 1985-02-20 | Bl Technology Limited | Control systems for continuously variable ratio transmissions |
GB2080452A (en) | 1980-07-17 | 1982-02-03 | Franklin John Warrender | Variable speed gear box |
US4391156A (en) | 1980-11-10 | 1983-07-05 | William R. Loeffler | Electric motor drive with infinitely variable speed transmission |
US4382186A (en) | 1981-01-12 | 1983-05-03 | Energy Sciences Inc. | Process and apparatus for converged fine line electron beam treatment of objects |
US4382188A (en) | 1981-02-17 | 1983-05-03 | Lockheed Corporation | Dual-range drive configurations for synchronous and induction generators |
US4526255A (en) | 1981-03-03 | 1985-07-02 | J. I. Case Company | Fluid drive transmission employing lockup clutch |
US4631469A (en) | 1981-04-14 | 1986-12-23 | Honda Giken Kogyo Kabushiki Kaisha | Device for driving electrical current generator for use in motorcycle |
JPS5814872U (en) | 1981-07-20 | 1983-01-29 | 株式会社森本製作所 | Automatic thread cutting device for sewing machine |
EP0073475B1 (en) | 1981-08-27 | 1988-02-03 | Nissan Motor Co., Ltd. | Control apparatus and method for engine-continuously variable transmission |
JPS5865361A (en) | 1981-10-09 | 1983-04-19 | Mitsubishi Electric Corp | Roller speed change gear |
JPS5831883Y2 (en) | 1981-10-29 | 1983-07-14 | 秀夫 椿 | Electroless plating device for thin plates with through holes |
JPS5899548A (en) | 1981-12-10 | 1983-06-13 | Honda Motor Co Ltd | Belt type infinitely variable gear |
US4700581A (en) | 1982-02-05 | 1987-10-20 | William R. Loeffler | Single ball traction drive assembly |
US4459873A (en) | 1982-02-22 | 1984-07-17 | Twin Disc, Incorporated | Marine propulsion system |
ATE21957T1 (en) | 1982-02-25 | 1986-09-15 | Fiat Auto Spa | CONTINUOUSLY PLANETARY GEAR WITH ROTARY DOUBLE TAPER ROLLERS. |
JPS5926657A (en) | 1982-08-04 | 1984-02-10 | Toyota Motor Corp | Control apparatus for vehicle equipped with stepless transmission type power transmitting mechanism |
US4501172A (en) | 1982-08-16 | 1985-02-26 | Excelermatic Inc. | Hydraulic speed control arrangement for an infinitely variable transmission |
JPS5969565A (en) | 1982-10-13 | 1984-04-19 | Mitsubishi Electric Corp | Stepless speed change gear |
JPS5969565U (en) | 1982-10-29 | 1984-05-11 | コニカ株式会社 | Video camera |
JPS59144826A (en) | 1983-02-02 | 1984-08-20 | Nippon Denso Co Ltd | One-way clutch |
JPS59190557A (en) | 1983-04-13 | 1984-10-29 | Tokyo Gijutsu Kenkyusho:Kk | Friction ball type stepless transmission |
JPS59217051A (en) | 1983-05-23 | 1984-12-07 | Toyota Motor Corp | Control for stepless speed change gear for car |
JPS59190557U (en) | 1983-06-01 | 1984-12-18 | 東芝テック株式会社 | Printer paper detection device |
JPS60153828U (en) | 1984-03-23 | 1985-10-14 | 三菱電機株式会社 | Engine auxiliary drive device |
US4781663A (en) | 1984-03-27 | 1988-11-01 | Reswick James B | Torque responsive automatic bicycle transmission with hold system |
US4617838A (en) | 1984-04-06 | 1986-10-21 | Nastec, Inc. | Variable preload ball drive |
JPS60247011A (en) | 1984-05-22 | 1985-12-06 | Nippon Seiko Kk | Engine accessory drive device |
US4569670A (en) | 1984-05-31 | 1986-02-11 | Borg-Warner Corporation | Variable pulley accessory drive |
US4567781A (en) | 1984-06-08 | 1986-02-04 | Norman Russ | Steady power |
JPS6131754A (en) | 1984-07-21 | 1986-02-14 | Yutaka Abe | Non-stage transmission with semispherical top |
JPS6153423A (en) | 1984-08-20 | 1986-03-17 | Diesel Kiki Co Ltd | Engine auxiliary machine driving controller |
JPS6153423U (en) | 1984-09-14 | 1986-04-10 | ||
US4585429A (en) | 1984-09-19 | 1986-04-29 | Yamaha Hatsudoki Kabushiki Kaisha | V-belt type continuously variable transmission |
US4735430A (en) | 1984-11-13 | 1988-04-05 | Philip Tomkinson | Racing bicycle having a continuously variable traction drive |
JPS61144466A (en) | 1984-12-17 | 1986-07-02 | Mitsubishi Electric Corp | Auxiliary equipment drive unit for engine |
JPH0646900B2 (en) | 1985-01-25 | 1994-06-22 | ヤンマー農機株式会社 | Nursery facility |
JPS61144466U (en) | 1985-02-28 | 1986-09-06 | ||
US4713976A (en) | 1985-03-22 | 1987-12-22 | Vern Heinrichs | Differential having a generally spherical differencing element |
JPS61228155A (en) | 1985-04-01 | 1986-10-11 | Mitsubishi Electric Corp | Auxiliary driving apparatus for engine |
JPH0330583Y2 (en) | 1985-04-17 | 1991-06-27 | ||
JPS61270552A (en) | 1985-05-25 | 1986-11-29 | Matsushita Electric Works Ltd | Transmission |
US4630839A (en) | 1985-07-29 | 1986-12-23 | Alenax Corp. | Propulsion mechanism for lever propelled bicycles |
GB8522747D0 (en) | 1985-09-13 | 1985-10-16 | Fellows T G | Transmission systems |
JPS6275170A (en) | 1985-09-28 | 1987-04-07 | Daihatsu Motor Co Ltd | Torque cam device |
JPH0426603Y2 (en) | 1985-10-31 | 1992-06-25 | ||
US4744261A (en) | 1985-11-27 | 1988-05-17 | Honeywell Inc. | Ball coupled compound traction drive |
JPS62127556A (en) | 1985-11-27 | 1987-06-09 | スペリ− コ−ポレイシヨン | Ball coupling composite traction drive |
US4717368A (en) | 1986-01-23 | 1988-01-05 | Aisin-Warner Kabushiki Kaisha | Stepless belt transmission |
US4838122A (en) | 1986-09-18 | 1989-06-13 | Bridgestone Cycle Co., Ltd. | Speed change device for bicycle |
JPH0776582B2 (en) | 1986-11-15 | 1995-08-16 | シンポ工業株式会社 | Vehicle automatic transmission |
JPS63160465A (en) | 1986-12-24 | 1988-07-04 | Nec Corp | Facsimile scanning system |
DE3706716A1 (en) | 1987-03-02 | 1988-09-15 | Planetroll Antriebe Gmbh | TRANSMISSION |
JPS63219953A (en) | 1987-03-10 | 1988-09-13 | Kubota Ltd | Disc type continuously variable transmission |
US4869130A (en) | 1987-03-10 | 1989-09-26 | Ryszard Wiecko | Winder |
JPH0722526Y2 (en) | 1987-04-09 | 1995-05-24 | 日産自動車株式会社 | Variable speed auxiliary drive control device for internal combustion engine |
JPS63262877A (en) | 1987-04-20 | 1988-10-31 | Semiconductor Energy Lab Co Ltd | Superconducting element |
EP0288080B1 (en) | 1987-04-24 | 1992-06-17 | Honda Giken Kogyo Kabushiki Kaisha | Belt type continuously variable transmission for vehicles |
JP2607889B2 (en) | 1987-08-04 | 1997-05-07 | 光洋精工株式会社 | Reduction motor |
JPS6460440A (en) | 1987-08-31 | 1989-03-07 | Fuji Heavy Ind Ltd | Control device for constant speed traveling of vehicle with continuously variable transmission |
JPH01286750A (en) | 1988-05-10 | 1989-11-17 | Fuji Heavy Ind Ltd | Generator for motorcar |
JP2708469B2 (en) | 1988-06-01 | 1998-02-04 | マツダ株式会社 | Engine charging and generating equipment |
US5025685A (en) | 1988-07-29 | 1991-06-25 | Honda Giken Kogyo Kabushiki Kaisha | Controlling device for non-stage transmission for vehicles |
US4964312A (en) | 1988-10-17 | 1990-10-23 | Excelermatic Inc. | Infinitely variable traction roller transmission |
US5020384A (en) | 1988-10-17 | 1991-06-04 | Excelermatic Inc. | Infinitely variable traction roller transmission |
JPH02130224A (en) | 1988-11-09 | 1990-05-18 | Mitsuboshi Belting Ltd | Auxiliary machinery driving device |
JPH02157483A (en) | 1988-12-07 | 1990-06-18 | Nippon Seiko Kk | Wind power generating device |
JP2734583B2 (en) | 1988-12-16 | 1998-03-30 | 日産自動車株式会社 | Transmission control device for continuously variable transmission |
JPH02182593A (en) | 1989-01-10 | 1990-07-17 | Shimpo Ind Co Ltd | Automatic speed change device for motorcycle |
JPH0650358Y2 (en) | 1989-01-27 | 1994-12-21 | 共同印刷株式会社 | Powder packaging container |
US5006093A (en) | 1989-02-13 | 1991-04-09 | Toyota Jidosha Kabushiki Kaisha | Hydraulic control apparatus for vehicle power transmitting system having continuously variable transmission |
JPH02271142A (en) | 1989-04-12 | 1990-11-06 | Nippondenso Co Ltd | Frictional type continuously variable transmission |
JP2568684B2 (en) | 1989-04-25 | 1997-01-08 | 日産自動車株式会社 | Friction wheel type continuously variable transmission |
JPH0826924B2 (en) | 1989-09-06 | 1996-03-21 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
JPH03149442A (en) | 1989-11-02 | 1991-06-26 | Mitsuo Okamoto | Friction type continuously variable transmission |
JPH0742799Y2 (en) | 1989-11-16 | 1995-10-04 | 武藤工業株式会社 | Backlight type coordinate analyzer |
US5044214A (en) | 1989-12-11 | 1991-09-03 | Barber Jr John S | Toroidal transmission with split torque and equalization planetary drive |
DE3940919A1 (en) | 1989-12-12 | 1991-06-13 | Fichtel & Sachs Ag | DRIVE HUB WITH CONTINUOUSLY ADJUSTABLE FRICTION GEARBOX |
ATE121884T1 (en) | 1989-12-12 | 1995-05-15 | Ascom Tech Ag | TRANSMISSION DEVICE WITH AN OPTICAL TRANSMISSION LINE. |
JPH03223555A (en) | 1990-01-26 | 1991-10-02 | Nippon Seiko Kk | Troidal type continuously variable transmission |
EP0448223B1 (en) | 1990-02-19 | 1996-06-26 | Canon Kabushiki Kaisha | Process for forming metal deposited film containing aluminium as main component by use of alkyl aluminum hydride |
CN1054340A (en) | 1990-02-24 | 1991-09-04 | 李培基 | The differential variable-frequency generating set |
JP2832283B2 (en) | 1990-04-13 | 1998-12-09 | 富士重工業株式会社 | Control device for continuously variable transmission |
US5059158A (en) | 1990-05-08 | 1991-10-22 | E.B.T., Inc. | Electronic transmission control system for a bicycle |
US5121654A (en) | 1990-09-04 | 1992-06-16 | Hector G. Fasce | Propulsion and transmission mechanism for bicycles, similar vehicles and exercise apparatus |
JPH04151053A (en) | 1990-10-12 | 1992-05-25 | Takashi Takahashi | Traction type gear shifter |
JPH04166619A (en) | 1990-10-30 | 1992-06-12 | Mazda Motor Corp | Accessory driving device in power unit |
US5125677A (en) | 1991-01-28 | 1992-06-30 | Ogilvie Frank R | Human powered machine and conveyance with reciprocating pedals |
US5236211A (en) | 1991-02-08 | 1993-08-17 | Ohannes Meguerditchian | Drive system |
US5156412A (en) | 1991-02-08 | 1992-10-20 | Ohannes Meguerditchian | Rectilinear pedal movement drive system |
JPH04272553A (en) | 1991-02-26 | 1992-09-29 | Suzuki Motor Corp | Friction continuously variable transmission |
US5562564A (en) | 1991-03-14 | 1996-10-08 | Synkinetics, Inc. | Integral balls and cams type motorized speed converter with bearings arrangement |
JPH04327055A (en) | 1991-04-23 | 1992-11-16 | Nissan Motor Co Ltd | Continuously variable transmission |
JP2666608B2 (en) | 1991-05-28 | 1997-10-22 | 日産自動車株式会社 | Friction wheel type continuously variable transmission |
DE4120540C1 (en) | 1991-06-21 | 1992-11-05 | Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De | |
DE4127030A1 (en) | 1991-08-16 | 1993-02-18 | Fichtel & Sachs Ag | DRIVE HUB WITH CONTINUOUSLY ADJUSTABLE GEAR RATIO |
DE4126993A1 (en) | 1991-08-16 | 1993-02-18 | Fichtel & Sachs Ag | Drive hub for a vehicle, especially a bicycle, with a continuously variable transmission ratio. |
DE4127043A1 (en) | 1991-08-16 | 1993-02-18 | Fichtel & Sachs Ag | DRIVE HUB WITH CONTINUOUSLY ADJUSTABLE GEAR RATIO |
JPH0792107B2 (en) | 1991-09-26 | 1995-10-09 | エヌティエヌ株式会社 | Torque limiter |
JP3200901B2 (en) | 1991-12-20 | 2001-08-20 | 株式会社日立製作所 | Electric vehicle drive |
US5138894A (en) | 1992-01-06 | 1992-08-18 | Excelermatic Inc. | Axial loading cam arrangement in or for a traction roller transmission |
JPH08500413A (en) | 1992-03-17 | 1996-01-16 | エリックス リミテッド | Continuously variable transmission |
JPH0650358A (en) | 1992-07-30 | 1994-02-22 | Ntn Corp | Torque limitter equipped with automatic reset function |
JPH0650169A (en) | 1992-07-31 | 1994-02-22 | Koyo Seiko Co Ltd | Gear shift unit for driving engine auxiliary machine |
TW218909B (en) | 1992-09-02 | 1994-01-11 | Song-Tyan Uen | A continuous transmission of eccentric slide block clutch type |
JPH0650169Y2 (en) | 1992-10-19 | 1994-12-21 | 池上金型工業株式会社 | Multiple molding die device |
CA2085022C (en) | 1992-12-10 | 1998-12-08 | Irwin W. Knight | Transmission having torque converter and planetary gear train |
US5330396A (en) | 1992-12-16 | 1994-07-19 | The Torax Company, Inc. | Loading device for continuously variable transmission |
US5451070A (en) | 1993-05-26 | 1995-09-19 | Lindsay; Stuart M. W. | Treadle drive system with positive engagement clutch |
IL106440A0 (en) | 1993-07-21 | 1993-11-15 | Ashot Ashkelon Ind Ltd | Wind turbine transmission apparatus |
JPH0742799A (en) | 1993-08-02 | 1995-02-10 | Koyo Seiko Co Ltd | Auxiliary driving device |
US5385514A (en) | 1993-08-11 | 1995-01-31 | Excelermalic Inc. | High ratio planetary transmission |
US5375865A (en) | 1993-09-16 | 1994-12-27 | Terry, Sr.; Maurice C. | Multiple rider bicycle drive line system including multiple continuously variable transmissions |
US5664636A (en) | 1993-10-29 | 1997-09-09 | Yamaha Hatsudoki Kabushiki Kaisha | Vehicle with electric motor |
JPH07133857A (en) | 1993-11-10 | 1995-05-23 | Mitsubishi Heavy Ind Ltd | Continuously variable transmission for normal and reverse rotation |
JPH07139600A (en) | 1993-11-15 | 1995-05-30 | Mazda Motor Corp | Toroidal type continuously variable transmission |
JP3448337B2 (en) * | 1994-03-17 | 2003-09-22 | 川崎重工業株式会社 | Hydraulic continuously variable transmission |
WO1995030848A1 (en) | 1994-05-04 | 1995-11-16 | Jean Valdenaire | Automatic continuously variable positive mechanical transmission and method for actuating same |
US5746676A (en) | 1994-05-31 | 1998-05-05 | Ntn Corporation | Friction type continuously variable transmission |
JP3456267B2 (en) | 1994-08-26 | 2003-10-14 | 日本精工株式会社 | Toroidal type continuously variable transmission |
JPH08135748A (en) | 1994-11-04 | 1996-05-31 | Isao Matsui | Automatic continuously variable transmitter |
CN1054340C (en) | 1994-11-21 | 2000-07-12 | 理想科学工业株式会社 | Rotary printing machine |
US5508574A (en) | 1994-11-23 | 1996-04-16 | Vlock; Alexander | Vehicle transmission system with variable speed drive |
US5799541A (en) | 1994-12-02 | 1998-09-01 | Fichtel & Sachs Ag | Twist-grip shifter for bicycles and a bicycle having a twist-grip shifter |
JPH08170706A (en) | 1994-12-14 | 1996-07-02 | Yasukuni Nakawa | Automatic continuously variable transmission |
JP3595887B2 (en) | 1995-03-07 | 2004-12-02 | 光洋精工株式会社 | Continuously variable transmission |
GB9505346D0 (en) | 1995-03-16 | 1995-05-03 | Fellows Thomas G | Improvements in or relating to continuously-variable-ratio transmissions |
JP3404973B2 (en) | 1995-03-29 | 2003-05-12 | 日産自動車株式会社 | Transmission control device for toroidal type continuously variable transmission |
JP2973920B2 (en) | 1995-05-24 | 1999-11-08 | トヨタ自動車株式会社 | Hybrid electric vehicle |
US6054844A (en) | 1998-04-21 | 2000-04-25 | The Regents Of The University Of California | Control method and apparatus for internal combustion engine electric hybrid vehicles |
JP3097505B2 (en) | 1995-07-13 | 2000-10-10 | トヨタ自動車株式会社 | Vehicle drive system |
JP3414059B2 (en) | 1995-07-19 | 2003-06-09 | アイシン・エィ・ダブリュ株式会社 | Vehicle drive system |
CN2245830Y (en) | 1995-07-30 | 1997-01-22 | 朱向阳 | Electromagnetism-planet driving infinitely speed variator |
US5690346A (en) | 1995-07-31 | 1997-11-25 | Keskitalo; Antti M. | Human powered drive-mechanism with versatile driving modes |
JPH0989064A (en) | 1995-09-27 | 1997-03-31 | Ntn Corp | Friction type continuously variable transmission |
RU2149787C1 (en) | 1995-11-20 | 2000-05-27 | Торотрак (Дивелопмент) Лимитед | Improvements for positioning servosystems or pertaining to such systems |
CA2238077A1 (en) | 1995-11-20 | 1997-05-29 | Christopher John Greenwood | Improvements in or relating to position servo systems |
JP3585617B2 (en) | 1995-12-28 | 2004-11-04 | 本田技研工業株式会社 | Power unit with continuously variable transmission |
DE59605832D1 (en) | 1996-01-11 | 2000-10-05 | Siemens Ag | CONTROL FOR A DEVICE IN A MOTOR VEHICLE |
JP3911749B2 (en) | 1996-03-29 | 2007-05-09 | マツダ株式会社 | Control device for automatic transmission |
JPH09267647A (en) | 1996-04-02 | 1997-10-14 | Honda Motor Co Ltd | Power transmitting mechanism for hybrid car |
DE19713423C5 (en) | 1996-04-03 | 2015-11-26 | Schaeffler Technologies AG & Co. KG | Device and method for actuating a transmission |
JP3314614B2 (en) | 1996-04-26 | 2002-08-12 | 日産自動車株式会社 | Loading cam for toroidal type continuously variable transmission |
JP3355941B2 (en) | 1996-07-16 | 2002-12-09 | 日産自動車株式会社 | Toroidal type continuously variable transmission |
JPH1061739A (en) | 1996-08-22 | 1998-03-06 | Mamoru Ishikuri | Continuously variable transmission |
JPH1078094A (en) | 1996-08-30 | 1998-03-24 | Mamoru Ishikuri | Continuously variable transmission using casing as pulley |
JPH1089435A (en) | 1996-09-11 | 1998-04-07 | Mamoru Ishikuri | Continuously variable transmission |
JP3480261B2 (en) | 1996-09-19 | 2003-12-15 | トヨタ自動車株式会社 | Electric vehicle drive |
JP3284060B2 (en) | 1996-09-20 | 2002-05-20 | 株式会社シマノ | Bicycle shift control method and shift control device thereof |
TW371646B (en) | 1996-09-26 | 1999-10-11 | Mistubishi Heavy Ind Ltd | Driving unit for an electric motor driven bicycle |
JPH10115355A (en) | 1996-10-08 | 1998-05-06 | Mamoru Ishikuri | Driven biaxial continuously variable transmission |
JPH10115356A (en) | 1996-10-11 | 1998-05-06 | Isuzu Motors Ltd | Planetary friction wheel type continuously variable transmission |
CN1167221A (en) | 1996-11-08 | 1997-12-10 | 邢万义 | Planetary gearing stepless speed regulator |
JP3385882B2 (en) | 1996-11-19 | 2003-03-10 | 日産自動車株式会社 | Hydraulic control device for toroidal type continuously variable transmission |
JPH10194186A (en) | 1997-01-13 | 1998-07-28 | Yamaha Motor Co Ltd | Motor-assisted bicycle |
JP3670430B2 (en) | 1997-02-05 | 2005-07-13 | 株式会社モリック | Electric bicycle drive device |
US6113513A (en) | 1997-02-26 | 2000-09-05 | Nsk Ltd. | Toroidal type continuously variable transmission |
JP3711688B2 (en) | 1997-03-22 | 2005-11-02 | マツダ株式会社 | Toroidal continuously variable transmission |
US6004239A (en) | 1997-03-31 | 1999-12-21 | Ntn Corporation | Friction type continuously variable speed changing mechanism |
JP3341633B2 (en) | 1997-06-27 | 2002-11-05 | 日産自動車株式会社 | Shift shock reduction device for vehicles with continuously variable transmission |
US5995895A (en) | 1997-07-15 | 1999-11-30 | Case Corporation | Control of vehicular systems in response to anticipated conditions predicted using predetermined geo-referenced maps |
US6101895A (en) | 1997-07-25 | 2000-08-15 | Shimano, Inc. | Grip for a bicycle shift control device |
US6119800A (en) | 1997-07-29 | 2000-09-19 | The Gates Corporation | Direct current electric vehicle drive |
JPH1163130A (en) | 1997-08-07 | 1999-03-05 | Nidec Shimpo Corp | Traction transmission gear |
JP3618967B2 (en) | 1997-08-08 | 2005-02-09 | 日産自動車株式会社 | Toroidal continuously variable transmission for vehicles |
US6000707A (en) | 1997-09-02 | 1999-12-14 | Linear Bicycles, Inc. | Linear driving apparatus |
US6419608B1 (en) | 1999-10-22 | 2002-07-16 | Motion Technologies, Llc | Continuously variable transmission |
TW401496B (en) | 1997-09-11 | 2000-08-11 | Honda Motor Co Ltd | Swash plate type continuously variable transmission |
JP3293531B2 (en) | 1997-09-19 | 2002-06-17 | 日産自動車株式会社 | Control device for continuously variable transmission |
JPH11108147A (en) | 1997-10-02 | 1999-04-20 | Nippon Seiko Kk | Continuously variable transmission |
US6261200B1 (en) | 1997-10-02 | 2001-07-17 | Nsk Ltd. | Continuously variable transmission |
DE19851995B4 (en) | 1997-11-11 | 2006-01-12 | Nsk Ltd. | Continuously adjustable toroidal transmission |
EP1029183B1 (en) | 1997-11-12 | 2008-01-02 | Folsom Technologies, Inc. | Hydraulic machine |
GB9727295D0 (en) | 1997-12-24 | 1998-02-25 | Torotrak Dev Ltd | Improvements in or relating to steplessly-variable-ratio transmission apparatus |
JP4056130B2 (en) | 1997-12-26 | 2008-03-05 | 松下電器産業株式会社 | Driving assistance device in a battery-assisted bicycle |
EP1045999B1 (en) | 1998-01-12 | 2003-10-08 | Orbital Traction Limited | A continuously variable transmission device |
JP4478225B2 (en) | 1998-01-26 | 2010-06-09 | 東京自動機工株式会社 | Transmission vehicle |
US6119539A (en) | 1998-02-06 | 2000-09-19 | Galaxy Shipping Enterprises, Inc. | Infinitely and continuously variable transmission system |
CA2259771C (en) | 1998-02-19 | 2003-04-01 | Hitachi, Ltd. | Transmission, and vehicle and bicycle using the same |
JPH11257479A (en) | 1998-03-10 | 1999-09-21 | Honda Motor Co Ltd | Control device for toroidal type continuously variable transmission |
JP3853963B2 (en) | 1998-03-20 | 2006-12-06 | 本田技研工業株式会社 | Power unit |
TW360184U (en) | 1998-04-18 | 1999-06-01 | Jun-Liang Chen | Improved structure for bicycle |
GB2337090A (en) | 1998-05-08 | 1999-11-10 | Torotrak Dev Ltd | Hydraulic control circuit for a continuously-variable ratio transmission |
JP3259684B2 (en) | 1998-06-22 | 2002-02-25 | 日産自動車株式会社 | Toroidal type continuously variable transmission for vehicles |
JP2000006877A (en) | 1998-06-22 | 2000-01-11 | Yamaha Motor Co Ltd | Power unit for motor-driven vehicle |
JP3409701B2 (en) | 1998-07-03 | 2003-05-26 | 日産自動車株式会社 | Control device for hybrid vehicle |
DE19831502A1 (en) | 1998-07-14 | 2000-01-20 | Zahnradfabrik Friedrichshafen | Control method for displacement or angle setting device in automobile e.g. for continuously variable drive transmission |
JP2000046135A (en) | 1998-07-28 | 2000-02-18 | Nissan Motor Co Ltd | Speed change control device for toroidal type continuously variable transmission |
US6076846A (en) | 1998-08-06 | 2000-06-20 | Clardy; Carl S. | Bicycle chest rest system |
DE19941705A1 (en) | 1998-09-09 | 2000-03-16 | Luk Lamellen & Kupplungsbau | Drive chain for an automobile, comprises an electric motor that can be used as a drive motor or generator |
JP3514142B2 (en) | 1998-11-04 | 2004-03-31 | 日産自動車株式会社 | Vehicle control device |
DE19851738A1 (en) | 1998-11-10 | 2000-05-18 | Getrag Getriebe Zahnrad | Drive train for motor vehicle has input for engine connection, wheel drive output and control element that is axially displaceable on shaft by at least one electromechanical actuator |
US6676549B1 (en) | 1998-12-18 | 2004-01-13 | Shimano, Inc. | Motion sensor for use with a bicycle sprocket assembly |
DE19858553A1 (en) | 1998-12-18 | 2000-06-21 | Zahnradfabrik Friedrichshafen | Infinitely-variable automotive gear reduces the load on the variator through the whole speed range, minimises noise and manufacturing costs |
JP3498901B2 (en) | 1998-12-25 | 2004-02-23 | 日産自動車株式会社 | Control device for belt-type continuously variable transmission |
US6095940A (en) | 1999-02-12 | 2000-08-01 | The Timken Company | Traction drive transmission |
DE19908250A1 (en) | 1999-02-25 | 2000-08-31 | Zahnradfabrik Friedrichshafen | Transmission ratio regulation for continuous automatic gearbox involves correction element taking account of internal and external system parameters in physical mathematical model |
DE60029662T2 (en) | 1999-03-16 | 2007-08-09 | Sumitomo Heavy Industries, Ltd. | Cycloidal gear and planetary friction gear |
US6325386B1 (en) | 1999-03-30 | 2001-12-04 | Shimano, Inc. | Rotatable seal assembly for a bicycle hub transmission |
US6312358B1 (en) | 1999-05-21 | 2001-11-06 | Advanced Technology Institute Of Commuter-Helicopter, Ltd. | Constant speed drive apparatus for aircraft generator and traction speed change apparatus |
JP3508690B2 (en) | 1999-06-02 | 2004-03-22 | 日産自動車株式会社 | Control device for continuously variable transmission with infinite transmission ratio |
DE19929424A1 (en) | 1999-06-26 | 2001-01-11 | Bosch Gmbh Robert | Friction wheel epicyclic gear with bevel gears |
JP2001027298A (en) | 1999-07-15 | 2001-01-30 | Nsk Ltd | Rotating shaft for toroidal type continuously variable transmission |
JP2001071986A (en) | 1999-09-03 | 2001-03-21 | Akebono Brake Ind Co Ltd | Automatic transmission for bicycle |
JP3547347B2 (en) | 1999-09-20 | 2004-07-28 | 株式会社日立製作所 | Motor generator for vehicles |
AU7707100A (en) | 1999-09-20 | 2001-04-24 | Transmission Technologies Corporation | Dual strategy control for a toroidal drive type continuously variable transmission |
JP2001107827A (en) | 1999-10-07 | 2001-04-17 | Toyota Motor Corp | Starting device and starting method for internal combustion engine |
JP3824821B2 (en) | 1999-10-08 | 2006-09-20 | 本田技研工業株式会社 | Regenerative control device for hybrid vehicle |
CN100520113C (en) * | 1999-11-12 | 2009-07-29 | 福尔布鲁克科技公司 | Continuously variable transmission |
CA2707702C (en) * | 1999-11-12 | 2011-05-24 | Motion Technologies, Llc | Continuously variable transmission |
JP2001165296A (en) | 1999-12-06 | 2001-06-19 | Nissan Motor Co Ltd | Transmission control device of continuously variable transmission with unlimited transmission gear ratio |
US6499373B2 (en) | 1999-12-17 | 2002-12-31 | Dale E. Van Cor | Stack of gears and transmission system utilizing the same |
US6375412B1 (en) | 1999-12-23 | 2002-04-23 | Daniel Christopher Dial | Viscous drag impeller components incorporated into pumps, turbines and transmissions |
DE60100404T2 (en) | 2000-01-07 | 2004-08-12 | Nissan Motor Co. Ltd. | Continuously variable transmission |
TW582363U (en) | 2000-01-14 | 2004-04-01 | World Ind Co Ltd | Apparatus for changing speed of bicycles |
JP3804383B2 (en) | 2000-01-19 | 2006-08-02 | トヨタ自動車株式会社 | Control device for vehicle having fuel cell |
JP2001234999A (en) | 2000-02-21 | 2001-08-31 | Advanced Technology Inst Of Commuter Helicopter Ltd | Axial force generating device and traction transmission |
JP3539335B2 (en) | 2000-03-10 | 2004-07-07 | トヨタ自動車株式会社 | Control device for vehicle with continuously variable transmission |
JP2001328466A (en) | 2000-03-14 | 2001-11-27 | Nissan Motor Co Ltd | Driving force control device for continuously variable transmission with infinite change gear ratio |
JP3696474B2 (en) | 2000-03-17 | 2005-09-21 | ジヤトコ株式会社 | Hydraulic control device for continuously variable transmission |
JP3628932B2 (en) | 2000-03-21 | 2005-03-16 | ジヤトコ株式会社 | Control device for continuously variable transmission |
JP3630297B2 (en) | 2000-03-23 | 2005-03-16 | 日産自動車株式会社 | Toroidal continuously variable transmission for automobiles |
KR200195466Y1 (en) | 2000-03-29 | 2000-09-01 | 비에이텍주식회사 | Continuous variable speed change transmission |
JP3738665B2 (en) | 2000-05-19 | 2006-01-25 | トヨタ自動車株式会社 | Hydraulic control device for transmission |
JP3785901B2 (en) | 2000-05-19 | 2006-06-14 | トヨタ自動車株式会社 | Shift control device for continuously variable transmission |
JP3855599B2 (en) | 2000-05-23 | 2006-12-13 | トヨタ自動車株式会社 | Control device for continuously variable transmission for vehicle |
US6492785B1 (en) | 2000-06-27 | 2002-12-10 | Deere & Company | Variable current limit control for vehicle electric drive system |
US6406399B1 (en) | 2000-07-28 | 2002-06-18 | The Timken Company | Planetary traction drive transmission |
US6371878B1 (en) | 2000-08-22 | 2002-04-16 | New Venture Gear, Inc. | Electric continuously variable transmission |
JP3672808B2 (en) | 2000-09-06 | 2005-07-20 | 松下電器産業株式会社 | Wireless communication terminal apparatus and interference canceling method |
DE10139119A1 (en) | 2000-09-08 | 2002-03-21 | Luk Lamellen & Kupplungsbau | Torque sensor for continuously variable transmission, has transmission body between input part receiving torque and output part providing corresponding pressure |
US6367833B1 (en) | 2000-09-13 | 2002-04-09 | Shimano, Inc. | Automatic shifting control device for a bicycle |
SE520904C2 (en) | 2000-09-28 | 2003-09-09 | Seco Tools Ab Publ | Drill with a countersunk connected to the chip channel in two halves |
JP3415601B2 (en) | 2000-10-23 | 2003-06-09 | 本田技研工業株式会社 | Control device for hybrid vehicle |
JP3726670B2 (en) * | 2000-10-25 | 2005-12-14 | 日産自動車株式会社 | Toroidal continuously variable transmission |
JP4254051B2 (en) | 2000-11-15 | 2009-04-15 | 日本精工株式会社 | Toroidal continuously variable transmission |
GB2369164A (en) | 2000-11-16 | 2002-05-22 | Torotrak Dev Ltd | Hydraulic control of a continuously-variable ratio transmission |
US6629590B2 (en) * | 2000-11-17 | 2003-10-07 | The Hilliard Corporation | Spring assembly for a bi-directional overrunning clutch |
JP2002250421A (en) | 2000-12-21 | 2002-09-06 | Kayseven Co Ltd | Variable speed change gear |
KR100368658B1 (en) | 2000-12-27 | 2003-01-24 | 현대자동차주식회사 | Clutch of vehicle |
DE60236844D1 (en) | 2001-01-03 | 2010-08-12 | Univ California | PROCESS FOR CONTROLLING THE OPERATING PROPERTIES |
JP3680739B2 (en) | 2001-02-06 | 2005-08-10 | 日産自動車株式会社 | Shift control device for continuously variable transmission |
JP3638876B2 (en) | 2001-03-01 | 2005-04-13 | 株式会社日立製作所 | Vehicle drive device and vehicle |
JP3942836B2 (en) | 2001-03-09 | 2007-07-11 | ジヤトコ株式会社 | Hydraulic oil cooling device for automatic transmission for vehicle |
US6482094B2 (en) | 2001-03-16 | 2002-11-19 | Schenck Rotec Gmbh | Self-aligning splined male shaft head and engagement method |
JP2002307956A (en) | 2001-04-11 | 2002-10-23 | Suzuki Motor Corp | Driving device for vehicle |
US6390945B1 (en) | 2001-04-13 | 2002-05-21 | Ratio Disc Corp. | Friction gearing continuously variable transmission |
JP3914999B2 (en) | 2001-04-19 | 2007-05-16 | 川崎重工業株式会社 | Shift control method and shift control apparatus |
JP3838052B2 (en) | 2001-05-08 | 2006-10-25 | 日産自動車株式会社 | Toroidal continuously variable transmission |
JP4378898B2 (en) | 2001-05-08 | 2009-12-09 | 日本精工株式会社 | Toroidal continuously variable transmission and continuously variable transmission |
DE10124265B4 (en) | 2001-05-18 | 2015-10-29 | Gustav Klauke Gmbh | pump |
US20020179348A1 (en) | 2001-05-30 | 2002-12-05 | Goro Tamai | Apparatus and method for controlling a hybrid vehicle |
GB0113523D0 (en) | 2001-06-04 | 2001-07-25 | Torotrak Dev Ltd | An Hydraulic control circuit for a continuosly variable transmission |
JP2002372114A (en) * | 2001-06-13 | 2002-12-26 | Ntn Corp | Frictional continuously variable transmission |
US6434960B1 (en) | 2001-07-02 | 2002-08-20 | Carrier Corporation | Variable speed drive chiller system |
US6814170B2 (en) | 2001-07-18 | 2004-11-09 | Nissan Motor Co., Ltd. | Hybrid vehicle |
JP3632634B2 (en) | 2001-07-18 | 2005-03-23 | 日産自動車株式会社 | Control device for hybrid vehicle |
JP2003028258A (en) | 2001-07-19 | 2003-01-29 | Nsk Ltd | Toroidal type continuously variable transmission |
JP2003056662A (en) | 2001-08-09 | 2003-02-26 | Nsk Ltd | Toroidal continuously variable transmission |
GB0121739D0 (en) | 2001-09-08 | 2001-10-31 | Milner Peter J | An improved continuously variable transmission |
JP3535490B2 (en) | 2001-10-19 | 2004-06-07 | 本田技研工業株式会社 | Power transmission device |
DE10155372A1 (en) | 2001-11-10 | 2003-05-22 | Bosch Gmbh Robert | System and method for specifying an engine torque and a transmission ratio in a vehicle with a continuously variable transmission |
JP3758151B2 (en) | 2001-11-22 | 2006-03-22 | 日本精工株式会社 | Toroidal continuously variable transmission |
JP2003161357A (en) | 2001-11-27 | 2003-06-06 | Ntn Corp | Speed-increasing gear for wind power generator |
JP4284905B2 (en) | 2001-12-04 | 2009-06-24 | 日産自動車株式会社 | Shift control device for continuously variable transmission |
TWI268320B (en) | 2001-12-04 | 2006-12-11 | Yamaha Motor Co Ltd | Continuously variable transmission and method of controlling it allowing for control of the axial position of a movable sheave without a sensor for measuring the axial position of the movable sheave on a rotational shaft and for stable control with the movable sheave being held in position |
JP2003194207A (en) | 2001-12-25 | 2003-07-09 | Nsk Ltd | Toroidal type continuously variable transmission |
JP3980352B2 (en) | 2001-12-28 | 2007-09-26 | ジヤトコ株式会社 | Torque shift compensator for toroidal continuously variable transmission |
JP3775660B2 (en) | 2002-01-17 | 2006-05-17 | 日本精工株式会社 | Cage for loading cam device of toroidal type continuously variable transmission |
CN1434229A (en) * | 2002-01-19 | 2003-08-06 | 刘亚军 | Multiple transmission pair stepless speed variation transmission device |
US6709355B2 (en) | 2002-01-28 | 2004-03-23 | O'hora Gerard M. | Continuously variable transmission |
CN101398068B (en) * | 2002-02-07 | 2011-07-06 | 舍弗勒技术两合公司 | Methods for regulating the gear ratio of an automatic power-branched transmission, and automatic power-branched transmission |
JP3654868B2 (en) | 2002-02-21 | 2005-06-02 | 株式会社シマノ | Bicycle shift control device and bicycle shift control method |
US7011592B2 (en) | 2002-03-08 | 2006-03-14 | Shimano, Inc. | Sprocket assembly for a bicycle |
US6839617B2 (en) | 2002-04-11 | 2005-01-04 | Nissan Motor Co., Ltd. | Extension of operating range of feedback in CVT ratio control |
US6740003B2 (en) | 2002-05-02 | 2004-05-25 | Shimano, Inc. | Method and apparatus for controlling a bicycle transmission |
JP4198937B2 (en) | 2002-05-17 | 2008-12-17 | 株式会社豊田中央研究所 | Toroidal CVT shift control device |
DE10223425A1 (en) | 2002-05-25 | 2003-12-04 | Bayerische Motoren Werke Ag | Infinitely variable friction roller toroidal gear |
JP4115166B2 (en) | 2002-05-31 | 2008-07-09 | 本田技研工業株式会社 | Bicycle with continuously variable transmission |
US6931316B2 (en) | 2002-06-05 | 2005-08-16 | Nissan Motor Co., Ltd. | Toroidal continuously variable transmission control apparatus |
JP4214720B2 (en) | 2002-06-10 | 2009-01-28 | 日産自動車株式会社 | Toroidal continuously variable transmission |
TWI235214B (en) | 2002-06-18 | 2005-07-01 | Yung-Tung Chen | Transmission system |
JP2004038722A (en) | 2002-07-05 | 2004-02-05 | Sunstar Eng Inc | Server system for providing power-assisted bicycle |
WO2004008003A1 (en) | 2002-07-10 | 2004-01-22 | Tadahiro Shimazu | Continuously variable transmission |
US6852064B2 (en) | 2002-07-18 | 2005-02-08 | Sauer-Danfoss, Inc. | Hydromechanical transmission electronic control system for high speed vehicles |
US6781510B2 (en) | 2002-07-24 | 2004-08-24 | Shimano, Inc. | Bicycle computer control arrangement and method |
US7303503B2 (en) * | 2002-08-02 | 2007-12-04 | Nsk Ltd. | Toroidal-type continuously variable transmission |
US20050233846A1 (en) | 2002-08-12 | 2005-10-20 | Green Arthur G | Variable radius continuously variable transmission |
CA2401474C (en) | 2002-09-05 | 2011-06-21 | Ecole De Technologie Superieure | Drive roller control for toric-drive transmission |
WO2004031620A2 (en) | 2002-09-30 | 2004-04-15 | Ulrich Rohs | Transmission |
US7111860B1 (en) | 2002-10-25 | 2006-09-26 | Jorge Grimaldos | Treadle scooter |
JP2004162652A (en) | 2002-11-14 | 2004-06-10 | Nsk Ltd | Wind power generation device |
JP3951904B2 (en) | 2002-11-29 | 2007-08-01 | 株式会社エクォス・リサーチ | Hybrid vehicle drive system |
DE60218186T2 (en) | 2002-12-06 | 2007-10-31 | Campagnolo S.R.L. | Electronic, servo-operated bicycle transmission and associated method |
JP4064806B2 (en) | 2002-12-19 | 2008-03-19 | ヤマハモーターエレクトロニクス株式会社 | Structure of synchronous motor for power assist |
JP3817516B2 (en) | 2002-12-26 | 2006-09-06 | 本田技研工業株式会社 | Drive control apparatus for hybrid vehicle |
US7028570B2 (en) | 2003-01-21 | 2006-04-18 | Honda Motor Co., Ltd. | Transmission |
US6868949B2 (en) | 2003-02-06 | 2005-03-22 | Borgwarner, Inc. | Start-up clutch assembly |
WO2004070233A1 (en) | 2003-02-10 | 2004-08-19 | Ntn Corporation | Traction drive type continuously variable transmission |
US6808053B2 (en) | 2003-02-21 | 2004-10-26 | New Venture Gear, Inc. | Torque transfer device having an electric motor/brake actuator and friction clutch |
JP4216093B2 (en) | 2003-02-26 | 2009-01-28 | 日本トムソン株式会社 | Manufacturing method of rolling bearing with solid lubricant |
US6991053B2 (en) | 2003-02-27 | 2006-01-31 | Ford Global Technologies, Llc | Closed-loop power control for hybrid electric vehicles |
CN100470091C (en) * | 2003-02-28 | 2009-03-18 | 福尔布鲁克科技公司 | Continuously variable transmission device |
CN1283258C (en) | 2003-03-11 | 2006-11-08 | 北京金桥时代生物医药研究发展中心 | Medicine for preventing fibrous liver and preparing method thereof |
EP1606134A4 (en) | 2003-03-19 | 2008-10-08 | Univ California | Method and system for controlling rate of change of ratio in a continuously variable transmission |
GB0307038D0 (en) | 2003-03-27 | 2003-04-30 | Torotrak Dev Ltd | System and method for controlling a continuously variable transmission |
JP2004301251A (en) | 2003-03-31 | 2004-10-28 | Koyo Seiko Co Ltd | Full toroidal-type continuously variable transmission |
NL1023319C2 (en) | 2003-05-01 | 2004-11-03 | Govers Henricus Johannes Anton | Road vehicle with auxiliary device. |
US7028475B2 (en) | 2003-05-20 | 2006-04-18 | Denso Corporation | Fluid machine |
JP2005003063A (en) | 2003-06-11 | 2005-01-06 | Nissan Motor Co Ltd | Vibration reducing device for internal combustion engine |
US7214159B2 (en) | 2003-08-11 | 2007-05-08 | Fallbrook Technologies Inc. | Continuously variable planetary gear set |
US7070530B2 (en) | 2003-08-26 | 2006-07-04 | The Timken Company | Method and apparatus for power flow management in electro-mechanical transmissions |
TWI225912B (en) | 2003-09-12 | 2005-01-01 | Ind Tech Res Inst | The mechanism for reverse gear of a belt-type continuously variable transmission |
JP4054739B2 (en) | 2003-09-24 | 2008-03-05 | 株式会社シマノ | Bicycle shift control device |
CN1300355C (en) | 2003-12-16 | 2007-02-14 | 兰州理工大学 | Aluminium and bronze alloy and process for preparing same |
JP2005188694A (en) | 2003-12-26 | 2005-07-14 | Koyo Seiko Co Ltd | Toroidal continuously variable transmission |
DE102004001278B4 (en) | 2004-01-07 | 2015-08-13 | Volkswagen Ag | Double clutch transmission for a motor vehicle |
US7316628B2 (en) | 2004-01-13 | 2008-01-08 | The Gates Corporation Ip Law Dept. | Two speed transmission and belt drive system |
US7010406B2 (en) | 2004-02-14 | 2006-03-07 | General Motors Corporation | Shift inhibit control for multi-mode hybrid drive |
US7086981B2 (en) | 2004-02-18 | 2006-08-08 | The Gates Corporation | Transmission and constant speed accessory drive |
US7029075B2 (en) | 2004-02-20 | 2006-04-18 | Shimano Inc. | Bicycle hub sealing assembly |
JP4588333B2 (en) | 2004-02-27 | 2010-12-01 | 株式会社モートロン・ドライブ | Rotating cam pressure regulator |
US7624656B2 (en) | 2004-04-01 | 2009-12-01 | Bhsci Llc | Continuously variable transmission |
JP4332796B2 (en) | 2004-04-19 | 2009-09-16 | トヨタ自動車株式会社 | Rotating electric machine having planetary gear transmission and method for manufacturing rotor support shaft constituting the same |
JP2007535715A (en) | 2004-05-01 | 2007-12-06 | ケイデンス デザイン システムズ インコーポレイテッド | Method and apparatus for designing an integrated circuit layout |
JP4151607B2 (en) | 2004-05-06 | 2008-09-17 | トヨタ自動車株式会社 | Belt type continuously variable transmission |
CN2714896Y (en) | 2004-05-08 | 2005-08-03 | 颜广博 | Electronic multifunctional stepless speed change device |
US7383748B2 (en) | 2004-05-28 | 2008-06-10 | Rankin Charles G | Automotive drivetrain having deflection compensation |
US7475758B2 (en) | 2004-06-18 | 2009-01-13 | Hayes Bicycle Group, Inc. | Bicycle disc brake having non-continuous spline surface for quick connection to or release from a wheel hub |
EP1610017A1 (en) | 2004-06-21 | 2005-12-28 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Torque transmitting apparatus and transmission comprising the same |
JP4729753B2 (en) | 2004-07-02 | 2011-07-20 | 独立行政法人海上技術安全研究所 | Manual wheelchair with continuously variable transmission mechanism |
JP2006046633A (en) | 2004-07-02 | 2006-02-16 | Yamaha Motor Co Ltd | Vehicle |
CN1985109B (en) | 2004-07-07 | 2010-10-27 | 易通公司 | Shift point strategy for hybrid electric vehicle transmission |
EP1774199B1 (en) | 2004-07-21 | 2013-06-12 | Fallbrook Intellectual Property Company LLC | Rolling traction planetary drive |
US7063195B2 (en) | 2004-07-27 | 2006-06-20 | Ford Global Technologies, Llc | Dual clutch assembly for a motor vehicle powertrain |
JP4553298B2 (en) | 2004-08-05 | 2010-09-29 | 本田技研工業株式会社 | Motor cooling structure for electric vehicles |
CA2479890A1 (en) | 2004-09-27 | 2006-03-27 | Samuel Beaudoin | High efficiency generator system and continuously variable transmission therefor |
US7727106B2 (en) | 2004-10-01 | 2010-06-01 | Pierre Maheu | Continuously variable transmission |
US8247371B2 (en) | 2004-10-14 | 2012-08-21 | Yale University | Therapy with Clostridium perfringens enterotoxin to treat ovarian and uterine cancer |
US7332881B2 (en) | 2004-10-28 | 2008-02-19 | Textron Inc. | AC drive system for electrically operated vehicle |
DE102004060351A1 (en) | 2004-12-15 | 2006-07-06 | Siemens Ag | Electric motor for rotation and axial movement |
JP2006200549A (en) | 2005-01-18 | 2006-08-03 | Fujitsu Ten Ltd | Control method for continuously variable transmission and its device |
TWI302501B (en) | 2005-02-15 | 2008-11-01 | Honda Motor Co Ltd | Power control unit |
CA2598641C (en) | 2005-02-22 | 2014-10-14 | Timken Us Corporation | Thrust bearing assembly |
JP2006283900A (en) | 2005-04-01 | 2006-10-19 | Nsk Ltd | Toroidal continuously variable transmission and continuously variable transmisson |
EP1710477B1 (en) | 2005-04-07 | 2009-02-25 | Getrag Ford Transmissions GmbH | Shift valve for a gear shift system of a transmission |
JP4867192B2 (en) | 2005-04-14 | 2012-02-01 | 三菱自動車工業株式会社 | Control device for continuously variable transmission |
US7473202B2 (en) | 2005-04-15 | 2009-01-06 | Eaton Corporation | Continuously variable dual mode transmission |
TW200637745A (en) | 2005-04-18 | 2006-11-01 | Sanyang Industry Co Ltd | Motorbike mixed power apparatus |
JP2006300241A (en) | 2005-04-21 | 2006-11-02 | Pentax Corp | One-way input/output rotation transmission mechanism |
DE102005031764A1 (en) | 2005-07-07 | 2007-01-18 | Zf Friedrichshafen Ag | A method of controlling a drive train of a vehicle having a prime mover and a transmission |
JP4157883B2 (en) | 2005-07-29 | 2008-10-01 | 株式会社シマノ | Cap member for bicycle internal gear shifting hub |
JP4814598B2 (en) | 2005-09-20 | 2011-11-16 | ヤンマー株式会社 | Hydraulic continuously variable transmission |
JP2007085514A (en) | 2005-09-26 | 2007-04-05 | Nidec-Shimpo Corp | Gearless drive mechanism |
US7343236B2 (en) | 2005-10-24 | 2008-03-11 | Autocraft Industries, Inc. | Electronic control system |
US7285068B2 (en) | 2005-10-25 | 2007-10-23 | Yamaha Hatsudoki Kabushiki Kaisha | Continuously variable transmission and engine |
JP4375321B2 (en) | 2005-10-31 | 2009-12-02 | トヨタ自動車株式会社 | Shift control device for continuously variable transmission |
TWM294598U (en) | 2005-11-08 | 2006-07-21 | Tuan Huei | Improved continuous stepless transmission structure |
US20070155567A1 (en) | 2005-11-22 | 2007-07-05 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7959533B2 (en) | 2005-12-09 | 2011-06-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
EP1811202A1 (en) | 2005-12-30 | 2007-07-25 | Fallbrook Technologies, Inc. | A continuously variable gear transmission |
US7882762B2 (en) | 2006-01-30 | 2011-02-08 | Fallbrook Technologies Inc. | System for manipulating a continuously variable transmission |
DK2002154T3 (en) | 2006-03-14 | 2014-01-13 | Fallbrook Ip Co Llc | GEAR SWITCH FOR SCOOTER |
WO2007106874A2 (en) | 2006-03-14 | 2007-09-20 | Autocraft Industries, Inc. | Improved wheelchair |
US20070228687A1 (en) | 2006-03-17 | 2007-10-04 | Rodger Parker | Bicycle propulsion mechanism |
JP4731505B2 (en) | 2006-03-17 | 2011-07-27 | ジヤトコ株式会社 | Hydraulic control device for belt type continuously variable transmission |
JP2007321931A (en) * | 2006-06-02 | 2007-12-13 | Nsk Ltd | Toroidal type continuously variable transmission |
CN102278200B (en) | 2006-06-26 | 2014-05-14 | 福博科知识产权有限责任公司 | Continuously variable transmission |
US7479090B2 (en) | 2006-07-06 | 2009-01-20 | Eaton Corporation | Method and apparatus for controlling a continuously variable transmission |
US7547264B2 (en) | 2006-08-14 | 2009-06-16 | Gm Global Technology Operations, Inc. | Starter alternator accessory drive system for a hybrid vehicle |
JP2008057614A (en) | 2006-08-30 | 2008-03-13 | Yamaha Motor Co Ltd | Belt type continuously variable transmission |
US8251863B2 (en) | 2006-09-01 | 2012-08-28 | Hdt Robotics, Inc. | Continuously variable transmission with multiple outputs |
EP2089642B1 (en) | 2006-11-08 | 2013-04-10 | Fallbrook Intellectual Property Company LLC | Clamping force generator |
JP4928239B2 (en) | 2006-11-28 | 2012-05-09 | 株式会社クボタ | Work vehicle |
US7860631B2 (en) | 2006-12-08 | 2010-12-28 | Sauer-Danfoss, Inc. | Engine speed control for a low power hydromechanical transmission |
FR2909938B1 (en) | 2006-12-15 | 2009-07-17 | Valeo Equip Electr Moteur | COUPLING BETWEEN THE THERMAL MOTOR AND THE AIR CONDITIONING COMPRESSOR OF A MOTOR VEHICLE |
JP2008155802A (en) | 2006-12-25 | 2008-07-10 | Toyota Motor Corp | Control device of vehicle driving device |
DE102008003047A1 (en) | 2007-01-24 | 2008-07-31 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Adjusting device for use in vehicle e.g. motor vehicle and drive train, has adjusting unit connected with sun wheel on axial drive in such manner that adjusting unit is axially adjusted relative to wheel during rotation |
US7641588B2 (en) | 2007-01-31 | 2010-01-05 | Caterpillar Inc. | CVT system having discrete selectable speed ranges |
WO2008095116A2 (en) | 2007-02-01 | 2008-08-07 | Fallbrook Technologies, Inc. | System and methods for control of transmission and/or prime mover |
WO2008100792A1 (en) | 2007-02-12 | 2008-08-21 | Fallbrook Technologies Inc. | Continuously variable transmissions and methods therefor |
JP5350274B2 (en) | 2007-02-16 | 2013-11-27 | フォールブルック インテレクチュアル プロパティー カンパニー エルエルシー | Infinitely variable transmission, continuously variable transmission, method, assembly, subassembly, and components therefor |
EP2573424A3 (en) | 2007-04-24 | 2017-07-26 | Fallbrook Intellectual Property Company LLC | Electric traction drives |
US7679207B2 (en) | 2007-05-16 | 2010-03-16 | V3 Technologies, L.L.C. | Augmented wind power generation system using continuously variable transmission and method of operation |
US9188206B2 (en) | 2007-06-06 | 2015-11-17 | Nsk Ltd. | Toroidal continuously variable transmission |
WO2008154437A1 (en) | 2007-06-11 | 2008-12-18 | Fallbrook Technologies Inc. | Continuously variable transmission |
KR20100046166A (en) | 2007-07-05 | 2010-05-06 | 폴브룩 테크놀로지즈 인크 | Continuously variable tranamission |
JP2008002687A (en) | 2007-09-25 | 2008-01-10 | Fujitsu Ten Ltd | Control device for continuously variable transmission |
JP5029290B2 (en) | 2007-10-29 | 2012-09-19 | 日産自動車株式会社 | Variable compression ratio engine |
US7887032B2 (en) | 2007-11-07 | 2011-02-15 | Fallbrook Technologies Inc. | Self-centering control rod |
CN103939602B (en) | 2007-11-16 | 2016-12-07 | 福博科知识产权有限责任公司 | Controller for variable speed drive |
US8321097B2 (en) | 2007-12-21 | 2012-11-27 | Fallbrook Intellectual Property Company Llc | Automatic transmissions and methods therefor |
WO2009111328A1 (en) | 2008-02-29 | 2009-09-11 | Fallbrook Technologies Inc. | Continuously and/or infinitely variable transmissions and methods therefor |
GB0805213D0 (en) | 2008-03-20 | 2008-04-30 | Torotrak Dev Ltd | An electric controller for a continuously variable transmission and a method of control of a continuously variable transmission |
WO2009137572A2 (en) | 2008-05-06 | 2009-11-12 | Alba Therapeutics Corporation | Inhibition of gliadin peptides |
US8317651B2 (en) | 2008-05-07 | 2012-11-27 | Fallbrook Intellectual Property Company Llc | Assemblies and methods for clamping force generation |
CN102112778B (en) | 2008-06-06 | 2013-10-16 | 福博科技术公司 | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
WO2009157920A1 (en) | 2008-06-23 | 2009-12-30 | Fallbrook Technologies Inc. | Continuously variable transmission |
WO2010017242A1 (en) | 2008-08-05 | 2010-02-11 | Fallbrook Technologies Inc. | Methods for control of transmission and prime mover |
JP4668307B2 (en) | 2008-08-29 | 2011-04-13 | ジヤトコ株式会社 | transmission |
JP4603607B2 (en) | 2008-09-18 | 2010-12-22 | 国立大学法人東北大学 | Wheel drive wheel drive swivel |
BRPI0805746B1 (en) | 2008-10-02 | 2020-06-09 | Luis Andre Parise | continuous transition exchange - ctc |
DK2342479T3 (en) | 2008-10-14 | 2013-08-26 | Fallbrook Ip Co Llc | Continuously variable transmission |
US8167759B2 (en) | 2008-10-14 | 2012-05-01 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20100181130A1 (en) | 2009-01-21 | 2010-07-22 | Wen-Cheng Chou | Dual-Drivetrain of Power-Assist Vehicle |
JP5158216B2 (en) | 2009-02-10 | 2013-03-06 | トヨタ自動車株式会社 | Continuously variable transmission mechanism and transmission using the continuously variable transmission mechanism |
RU2011140072A (en) | 2009-04-16 | 2013-05-27 | Фоллбрук Текнолоджиз Инк. (Сша/Сша) | STATOR ASSEMBLY AND GEAR SHIFTING MECHANISM FOR THE TRANSMISSION-FREE TRANSMISSION |
WO2010122646A1 (en) | 2009-04-23 | 2010-10-28 | トヨタ自動車株式会社 | Speed-change controller for vehicular transmissions |
US9080797B2 (en) | 2009-05-19 | 2015-07-14 | Carrier Corporation | Variable speed compressor |
ES2643067T3 (en) | 2009-10-08 | 2017-11-21 | Ultimate Transmissions Pty Ltd | Total Toroidal Traction Motor |
US8230961B2 (en) | 2009-11-04 | 2012-07-31 | Toyota Motor Engineering & Manufacturing North America, Inc. | Energy recovery systems for vehicles and wheels comprising the same |
GB0920546D0 (en) | 2009-11-24 | 2010-01-06 | Torotrak Dev Ltd | Drive mechanism for infinitely variable transmission |
US8172022B2 (en) | 2009-11-30 | 2012-05-08 | Toyota Motor Engineering & Manufacturing North America, Inc. | Energy recovery systems for vehicles and vehicle wheels comprising the same |
US8992376B2 (en) | 2010-02-22 | 2015-03-31 | Toyota Jidosha Kabushiki Kaisha | Power transmission device |
US8512195B2 (en) | 2010-03-03 | 2013-08-20 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
DE112010005401B8 (en) | 2010-03-18 | 2014-11-13 | Toyota Jidosha Kabushiki Kaisha | Continuously variable transmission |
WO2011121743A1 (en) | 2010-03-30 | 2011-10-06 | トヨタ自動車株式会社 | Engine start-up control device for hybrid vehicle |
US8581463B2 (en) | 2010-06-01 | 2013-11-12 | Lawrence Livermore National Laboratory, Llc | Magnetic bearing element with adjustable stiffness |
US8382631B2 (en) | 2010-07-21 | 2013-02-26 | Ford Global Technologies, Llc | Accessory drive and engine restarting system |
US20120035011A1 (en) | 2010-08-09 | 2012-02-09 | Menachem Haim | Electro mechanical bicycle derailleur actuator system and method |
NL2005297C2 (en) | 2010-09-01 | 2012-03-05 | Fides5 B V | BICYCLE WITH ELECTRIC DRIVE. |
US8888643B2 (en) | 2010-11-10 | 2014-11-18 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US8376889B2 (en) | 2010-12-07 | 2013-02-19 | Ford Global Technologies, Llc | Transmission producing continuously variable speed ratios |
CN103370560B (en) | 2010-12-23 | 2016-04-13 | 范戴尼超级涡轮有限公司 | Symmetrical traction drive, machinery-turbosupercharger and in symmetrical traction drive, transmit the method for rotating mechanical energy |
US8517888B1 (en) | 2011-01-07 | 2013-08-27 | Ernie Brookins | Mechanical power transmission system and method |
CN102762894B (en) | 2011-02-03 | 2016-05-04 | 日本精工株式会社 | Toroidal type stepless speed change device |
JP2012172685A (en) | 2011-02-17 | 2012-09-10 | Nsk Ltd | Toroidal type continuously variable transmission |
CN103608607B (en) * | 2011-03-29 | 2015-09-30 | 丰田自动车株式会社 | Stepless speed variator |
AU2012240435B2 (en) | 2011-04-04 | 2016-04-28 | Fallbrook Intellectual Property Company Llc | Auxiliary power unit having a continuously variable transmission |
DE102011016672A1 (en) | 2011-04-09 | 2012-10-11 | Peter Strauss | Stepless gearbox for e.g. pedal electric cycle, has frictional bodies whose rotational axis is inclined to main axis and lies tangential or perpendicular to imaginary cylindrical periphery of main axis |
JP5500118B2 (en) | 2011-04-18 | 2014-05-21 | トヨタ自動車株式会社 | Continuously variable transmission |
US8992389B2 (en) | 2011-08-04 | 2015-03-31 | Christianna Abel | Multi-directional adjustable exercise slide board |
JP5783260B2 (en) | 2011-09-21 | 2015-09-24 | トヨタ自動車株式会社 | Continuously variable transmission |
CN103797274B (en) | 2011-09-22 | 2016-06-15 | 丰田自动车株式会社 | Buncher |
CN107061653B (en) | 2012-01-23 | 2020-05-26 | 福博科知识产权有限责任公司 | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components thereof |
EP2893219A4 (en) | 2012-09-06 | 2016-12-28 | Dana Ltd | Transmission having a continuously or infinitely variable variator drive |
DE102012023551A1 (en) | 2012-12-01 | 2014-06-05 | Peter Strauss | Infinitely variable gear system for e.g. bicycles, has chain drive whose gear is located outside gear housing, and pinion bolt driven over chain of chain ring that is rotationally and axial fixedly connected to drive wheel of bicycle |
US8814739B1 (en) | 2013-03-14 | 2014-08-26 | Team Industries, Inc. | Continuously variable transmission with an axial sun-idler controller |
CN105121905A (en) | 2013-03-14 | 2015-12-02 | 德纳有限公司 | Ball type continuously variable transmission |
US8827856B1 (en) | 2013-03-14 | 2014-09-09 | Team Industries, Inc. | Infinitely variable transmission with an IVT stator controlling assembly |
CA2909565A1 (en) | 2013-04-19 | 2014-10-23 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
WO2014186732A1 (en) | 2013-05-17 | 2014-11-20 | Dana Limited | 3-mode front-wheel drive continuously variable planetary transmission with stacked gearsets |
DE102014007271A1 (en) | 2013-06-15 | 2014-12-18 | Peter Strauss | Stepless bottom bracket gearbox for LEVs (Light electric vehicles) with integrated electric motor |
JP2015227690A (en) | 2014-05-30 | 2015-12-17 | トヨタ自動車株式会社 | Continuously variable transmission |
JP5880624B2 (en) | 2014-05-30 | 2016-03-09 | トヨタ自動車株式会社 | Continuously variable transmission |
JP2015227691A (en) | 2014-05-30 | 2015-12-17 | トヨタ自動車株式会社 | Continuously variable transmission |
JP2016014435A (en) | 2014-07-02 | 2016-01-28 | 株式会社デンソー | Shift range switching control unit |
US9682744B2 (en) | 2014-07-30 | 2017-06-20 | Shimano Inc. | Bicycle shifting control apparatus |
DE102014221514A1 (en) | 2014-10-23 | 2016-04-28 | Robert Bosch Gmbh | Adjustable friction-ring gearbox for a motor-powered and / or pedal-operated vehicle |
JP2018511510A (en) | 2015-02-13 | 2018-04-26 | シヴィライズド・サイクルズ・インコーポレーティッド | Electric bicycle transmission system, method and apparatus |
US10400872B2 (en) | 2015-03-31 | 2019-09-03 | Fallbrook Intellectual Property Company Llc | Balanced split sun assemblies with integrated differential mechanisms, and variators and drive trains including balanced split sun assemblies |
US9896152B2 (en) * | 2015-05-25 | 2018-02-20 | Shimano Inc. | Bicycle transmission system |
US10030594B2 (en) | 2015-09-18 | 2018-07-24 | Dana Limited | Abuse mode torque limiting control method for a ball-type continuously variable transmission |
US10546052B2 (en) | 2015-10-12 | 2020-01-28 | Sugarcrm Inc. | Structured touch screen interface for mobile forms generation for customer relationship management (CRM) |
US10047861B2 (en) | 2016-01-15 | 2018-08-14 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
CN109154368B (en) | 2016-03-18 | 2022-04-01 | 福博科知识产权有限责任公司 | Continuously variable transmission, system and method |
JP6477656B2 (en) | 2016-10-14 | 2019-03-06 | トヨタ自動車株式会社 | Oil passage structure of power transmission device |
-
2008
- 2008-02-07 WO PCT/US2008/053347 patent/WO2008100792A1/en active Application Filing
- 2008-02-07 CN CN201410265955.XA patent/CN104121345B/en active Active
- 2008-02-07 US US12/526,770 patent/US20100093479A1/en not_active Abandoned
- 2008-02-07 CN CN200880010199.9A patent/CN101657653B/en active Active
- 2008-02-12 TW TW097104836A patent/TWI548824B/en active
-
2013
- 2013-06-27 US US13/928,779 patent/US9371894B2/en not_active Expired - Fee Related
-
2016
- 2016-06-20 US US15/186,898 patent/US10260607B2/en active Active
Patent Citations (120)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US575533A (en) * | 1897-01-19 | James philip ottaway | ||
US719595A (en) * | 1901-07-06 | 1903-02-03 | Jacob B Huss | Bicycle driving mechanism. |
US1175677A (en) * | 1914-10-24 | 1916-03-14 | Roderick Mcclure | Power-transmitting device. |
US1903228A (en) * | 1927-10-21 | 1933-03-28 | Gen Motors Corp | Frictional gearing |
US1793571A (en) * | 1929-12-14 | 1931-02-24 | Frank O Vaughn | Variable-speed drive |
US1847027A (en) * | 1930-02-19 | 1932-02-23 | Thomsen Thomas Peter | Change-speed gear |
US2109845A (en) * | 1932-07-23 | 1938-03-01 | Erban Operating Corp | Power transmission mechanism |
US2112763A (en) * | 1933-12-28 | 1938-03-29 | Cloudsley John Leslie | Variable speed power transmission mechanism |
US2030203A (en) * | 1934-05-31 | 1936-02-11 | Gen Motors Corp | Torque loading lash adjusting device for friction roller transmissions |
US2269434A (en) * | 1940-11-18 | 1942-01-13 | Cuyler W Brooks | Automatic transmission mechanism |
US2461258A (en) * | 1946-06-06 | 1949-02-08 | Cuyler W Brooks | Automatic transmission mechanism |
US2730904A (en) * | 1952-07-14 | 1956-01-17 | Rennerfelt Sven Bernhard | Continuously variable speed gears |
US2868038A (en) * | 1955-05-26 | 1959-01-13 | Liquid Controls Corp | Infinitely variable planetary transmission |
US2874592A (en) * | 1955-11-07 | 1959-02-24 | Mcculloch Motors Corp | Self-controlled variable speed planetary type drive |
US3487726A (en) * | 1966-07-04 | 1970-01-06 | Self Changing Gears Ltd | Auxiliary overdrive gear |
US3487727A (en) * | 1966-11-30 | 1970-01-06 | Bror Artur Gustafsson | Continuously variable speed variators |
US3707888A (en) * | 1970-07-31 | 1973-01-02 | Roller Gear Ltd | Variable speed transmission |
US3934493A (en) * | 1973-12-15 | 1976-01-27 | Raleigh Industries Limited | Epicyclic change speed gears |
US3866985A (en) * | 1974-03-04 | 1975-02-18 | Caterpillar Tractor Co | Track roller |
US4496051A (en) * | 1981-06-09 | 1985-01-29 | Ortner Georg J | Container with information-carrying element |
US4369667A (en) * | 1981-07-10 | 1983-01-25 | Vadetec Corporation | Traction surface cooling method and apparatus |
US4574649A (en) * | 1982-03-10 | 1986-03-11 | B. D. Yim | Propulsion and speed change mechanism for lever propelled bicycles |
US4494524A (en) * | 1982-07-19 | 1985-01-22 | Lee Wagner | Centrifugal heating unit |
US4651082A (en) * | 1985-04-03 | 1987-03-17 | Mitsubishi Denki Kabushiki Kaisha | Generating apparatus with an adjustable speed change mechanism |
US4900046A (en) * | 1987-10-06 | 1990-02-13 | Aranceta Angoitia Inaki | Transmission for bicycles |
US4909101A (en) * | 1988-05-18 | 1990-03-20 | Terry Sr Maurice C | Continuously variable transmission |
US5601301A (en) * | 1989-12-18 | 1997-02-11 | Liu; Qingshan | Drive system for muscle-powered equipment and vehicles, in particular bicycles |
US5401221A (en) * | 1990-08-17 | 1995-03-28 | Torotrak (Development) Limited | Transmission of the toroidal-race, rolling-traction type having a mixer and a reducer epicyclic type gearing with clutches brakes |
US5379661A (en) * | 1992-03-13 | 1995-01-10 | Nsk Ltd. | Loading cam device |
US5489003A (en) * | 1992-05-29 | 1996-02-06 | Honda Giken Kogyo Kabushiki Kaisha | Electric vehicle |
US5387000A (en) * | 1992-07-22 | 1995-02-07 | Sato; Yasunori | Hydraulic drive system for bicycles and the like |
US5564998A (en) * | 1993-01-18 | 1996-10-15 | Torotrak (Development) Limited | Continuously-variable-ratio-transmissions |
US5383677A (en) * | 1994-03-14 | 1995-01-24 | Thomas; Timothy N. | Bicycle body support apparatus |
US5607373A (en) * | 1994-04-28 | 1997-03-04 | Nissan Motor Co., Ltd. | CVT ratio rate control as a function of throttle release rate |
US6042132A (en) * | 1995-03-13 | 2000-03-28 | Sakae Co., Ltd. | Bicycle and bicycle speed change operation assembly |
US5888160A (en) * | 1996-11-13 | 1999-03-30 | Nsk Ltd. | Continuously variable transmission |
US6019701A (en) * | 1997-03-07 | 2000-02-01 | Nissan Motor Co., Ltd. | Shift control apparatus for continuously variable transmission |
US6186922B1 (en) * | 1997-03-27 | 2001-02-13 | Synkinetics, Inc. | In-line transmission with counter-rotating outputs |
US6029990A (en) * | 1997-05-13 | 2000-02-29 | Gt Bicycles, Inc. | Direct drive bicycle |
US6171210B1 (en) * | 1997-08-12 | 2001-01-09 | Nsk Ltd. | Toroidal type continuous variable transmission system |
US7175564B2 (en) * | 1997-09-02 | 2007-02-13 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7160222B2 (en) * | 1997-09-02 | 2007-01-09 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7156770B2 (en) * | 1997-09-02 | 2007-01-02 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7014591B2 (en) * | 1997-09-02 | 2006-03-21 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7011601B2 (en) * | 1997-09-02 | 2006-03-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7163485B2 (en) * | 1997-09-02 | 2007-01-16 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7320660B2 (en) * | 1997-09-02 | 2008-01-22 | Fallbrook Technologies Inc. | Continuously variable transmission |
US6676559B2 (en) * | 1997-09-02 | 2004-01-13 | Motion Technologies, Llc | Continuously variable transmission |
US6672418B1 (en) * | 1998-06-29 | 2004-01-06 | Yamaha Hatsudoki Kabushiki Kaisha | Electric motor-assisted vehicle |
US6251038B1 (en) * | 1998-10-21 | 2001-06-26 | Nsk Ltd. | Continuously variable transmission unit |
US6258003B1 (en) * | 1999-02-15 | 2001-07-10 | Nissan Motor Co., Ltd. | Infinite speed ratio transmission device and assembly method thereof |
US6099431A (en) * | 1999-05-06 | 2000-08-08 | Ford Global Technologies, Inc. | Method for operating a traction drive automatic transmission for automotive vehicles |
US6045477A (en) * | 1999-06-14 | 2000-04-04 | General Motors Corporation | Continuously variable multi-range powertrain with a geared neutral |
US20030036456A1 (en) * | 2000-03-23 | 2003-02-20 | Alfred Skrabs | Method for assembling a planetary gear unit in a precise position |
US6659901B2 (en) * | 2000-03-30 | 2003-12-09 | Nissan Motor Co., Ltd. | Infinite speed ratio continuously variable transmission |
US20020045511A1 (en) * | 2000-05-05 | 2002-04-18 | Daimlerchrysler Ag. | Continuously variable vehicle transmission |
US6358178B1 (en) * | 2000-07-07 | 2002-03-19 | General Motors Corporation | Planetary gearing for a geared neutral traction drive |
US20020028722A1 (en) * | 2000-07-21 | 2002-03-07 | Nissan Motor Co., Ltd. | Control of infinitely variable transmission |
US6494805B2 (en) * | 2000-07-27 | 2002-12-17 | Honda Giken Kogyo Kabushiki Kaisha | Continuously variable transmission system for vehicle |
US20020019285A1 (en) * | 2000-08-11 | 2002-02-14 | Steffen Henzler | Transmission arrangement |
US6679109B2 (en) * | 2000-11-30 | 2004-01-20 | Zf Batavia Llc | Acoustic recognition of variator slip of a continuously variable transmission |
US7029418B2 (en) * | 2000-12-28 | 2006-04-18 | Toyota Jidosha Kabushiki Kaisha | Toroidal type continuoulsy variable transmission |
US6689012B2 (en) * | 2001-04-26 | 2004-02-10 | Motion Technologies, Llc | Continuously variable transmission |
US7166058B2 (en) * | 2001-04-26 | 2007-01-23 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7192381B2 (en) * | 2001-04-26 | 2007-03-20 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7163486B2 (en) * | 2001-04-26 | 2007-01-16 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7166057B2 (en) * | 2001-04-26 | 2007-01-23 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7175566B2 (en) * | 2001-04-26 | 2007-02-13 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7510499B2 (en) * | 2001-04-26 | 2009-03-31 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7175565B2 (en) * | 2001-04-26 | 2007-02-13 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7172529B2 (en) * | 2001-04-26 | 2007-02-06 | Fallbrook Technologies Inc. | Continuously variable transmission |
US6532890B2 (en) * | 2001-06-14 | 2003-03-18 | Ad-Ii Engineering Inc. | Speed indicator for a shifting device of bicycle |
US20030022753A1 (en) * | 2001-07-26 | 2003-01-30 | Toyota Jidosha Kabushiki Kaisha | Control system and method for vehicle having continuously variable transmission |
US6723016B2 (en) * | 2001-09-27 | 2004-04-20 | Jatco Ltd | Torque split infinitely variable transmission |
US7077777B2 (en) * | 2001-10-05 | 2006-07-18 | Nsk Ltd. | Continuously variable transmission |
US6991579B2 (en) * | 2001-10-19 | 2006-01-31 | Nsk Ltd. | Toroidal type continuously variable transmission |
US6932739B2 (en) * | 2001-12-25 | 2005-08-23 | Nsk Ltd. | Continuously variable transmission apparatus |
US20030216216A1 (en) * | 2002-04-18 | 2003-11-20 | Nsk Ltd. | Apparatus and method for controlling transmission ratio of toroidal-type continuously variable transmission unit for continuously variable transmission apparatus |
US6849020B2 (en) * | 2002-08-07 | 2005-02-01 | Jatco Ltd | Continuously variable power-split transmission |
US20040058772A1 (en) * | 2002-08-23 | 2004-03-25 | Nsk Ltd. | Toroidal-type continuously variable transmission and continuously variable transmission apparatus |
US6682432B1 (en) * | 2002-09-04 | 2004-01-27 | Kinzou Shinozuka | Multiple shaft diameter flexible coupling system |
US20060052204A1 (en) * | 2002-09-05 | 2006-03-09 | Harald Eckert | Electromagnetic selection device for a two-stage planetary gear set |
US20040082421A1 (en) * | 2002-10-24 | 2004-04-29 | Jurgen Wafzig | Split performance power train |
US6958029B2 (en) * | 2002-11-28 | 2005-10-25 | Nsk Ltd. | Continuously variable transmission apparatus |
US7217216B2 (en) * | 2002-12-05 | 2007-05-15 | Nsk Ltd. | Continuously variable transmission apparatus |
US7094171B2 (en) * | 2002-12-05 | 2006-08-22 | Nsk Ltd. | Continuously variable transmission apparatus |
US6991575B2 (en) * | 2003-02-14 | 2006-01-31 | Nsk Ltd | Continuously variable transmission apparatus |
US7169076B2 (en) * | 2003-02-28 | 2007-01-30 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7011600B2 (en) * | 2003-02-28 | 2006-03-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20120035016A1 (en) * | 2003-02-28 | 2012-02-09 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7166056B2 (en) * | 2003-02-28 | 2007-01-23 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7322901B2 (en) * | 2003-02-28 | 2008-01-29 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7160220B2 (en) * | 2003-07-14 | 2007-01-09 | Nsk Ltd. | Continuously variable transmission apparatus |
US7166052B2 (en) * | 2003-08-11 | 2007-01-23 | Fallbrook Technologies Inc. | Continuously variable planetary gear set |
US7481736B2 (en) * | 2003-08-11 | 2009-01-27 | Fallbrook Technologies Inc. | Continuously variable planetary gear set |
US20070149342A1 (en) * | 2004-04-30 | 2007-06-28 | Ruehle Guenter | Toroidal transmission |
US7347801B2 (en) * | 2004-04-30 | 2008-03-25 | Getrag Getriebe-Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Toroidal transmission |
US7591755B2 (en) * | 2004-05-11 | 2009-09-22 | Getrag Getriebe-Und Zahnradfabrik Hermann Hagenmeyer Gmbh | Hydraulic circuit for a toroidal transmission |
US20080034585A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039273A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080032853A1 (en) * | 2004-10-05 | 2008-02-07 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039271A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039272A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039270A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039275A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039274A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039277A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080040008A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080034586A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039269A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039276A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080032854A1 (en) * | 2004-10-05 | 2008-02-07 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080032852A1 (en) * | 2004-10-05 | 2008-02-07 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080046403A1 (en) * | 2004-12-23 | 2008-02-21 | Microsoft Corporation | Easy-to-use data report specification |
US7238139B2 (en) * | 2005-01-06 | 2007-07-03 | Ford Global Technologies, Inc. | Electric and hybrid electric powertrain for motor vehicles |
US8142323B2 (en) * | 2005-03-31 | 2012-03-27 | Torotrak (Development) Limited | Continuously variable transmission |
US20070004552A1 (en) * | 2005-06-30 | 2007-01-04 | Honda Motor Co., Ltd. | Continuously variable transmission controller |
US20070049450A1 (en) * | 2005-08-24 | 2007-03-01 | Miller Donald C | Continuously variable transmission |
US20120043841A1 (en) * | 2005-10-28 | 2012-02-23 | Fallbrook Technologies Inc. | Electromotive drives |
US20100056322A1 (en) * | 2008-08-26 | 2010-03-04 | Fallbrook Technologies Inc. | Continuously variable transmission |
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US8171636B2 (en) | 2004-10-05 | 2012-05-08 | Fallbrook Technologies Inc. | Method of manufacturing a stator of a cage for a continuously variable transmission (CVT) |
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US20080039273A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
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US20080039277A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039270A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039275A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039271A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080039272A1 (en) * | 2004-10-05 | 2008-02-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US20080032854A1 (en) * | 2004-10-05 | 2008-02-07 | Fallbrook Technologies Inc. | Continuously variable transmission |
US8133149B2 (en) | 2004-10-05 | 2012-03-13 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7909727B2 (en) | 2004-10-05 | 2011-03-22 | Fallbrook Technologies Inc. | Continuously variable transmission |
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US7963880B2 (en) | 2004-10-05 | 2011-06-21 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7967719B2 (en) | 2004-10-05 | 2011-06-28 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7976426B2 (en) | 2004-10-05 | 2011-07-12 | Fallbrook Technologies Inc. | Continuously variable transmission |
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US9611921B2 (en) | 2012-01-23 | 2017-04-04 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
US10428915B2 (en) | 2012-01-23 | 2019-10-01 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
US9541179B2 (en) | 2012-02-15 | 2017-01-10 | Dana Limited | Transmission and driveline having a tilting ball variator continuously variable transmission |
CN102817984A (en) * | 2012-08-27 | 2012-12-12 | 北京理工大学 | Axial-loading biconical traction drive device |
US9556941B2 (en) | 2012-09-06 | 2017-01-31 | Dana Limited | Transmission having a continuously or infinitely variable variator drive |
US20150204430A1 (en) * | 2012-09-07 | 2015-07-23 | Dana Limited | Ball type cvt with powersplit paths |
US9599204B2 (en) | 2012-09-07 | 2017-03-21 | Dana Limited | Ball type CVT with output coupled powerpaths |
US9556943B2 (en) | 2012-09-07 | 2017-01-31 | Dana Limited | IVT based on a ball-type CVP including powersplit paths |
US9052000B2 (en) | 2012-09-07 | 2015-06-09 | Dana Limited | Ball type CVT/IVT including planetary gear sets |
US9689477B2 (en) | 2012-09-07 | 2017-06-27 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
US8986150B2 (en) | 2012-09-07 | 2015-03-24 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
US9353842B2 (en) * | 2012-09-07 | 2016-05-31 | Dana Limited | Ball type CVT with powersplit paths |
US9416858B2 (en) | 2012-09-07 | 2016-08-16 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
US9638296B2 (en) | 2012-09-07 | 2017-05-02 | Dana Limited | Ball type CVT including a direct drive mode |
JP2015527554A (en) * | 2012-09-07 | 2015-09-17 | デーナ リミテッド | Ball CVT including direct drive mode |
US10006527B2 (en) | 2012-09-07 | 2018-06-26 | Dana Limited | Ball type continuously variable transmission/infinitely variable transmission |
US10088026B2 (en) | 2012-09-07 | 2018-10-02 | Dana Limited | Ball type CVT with output coupled powerpaths |
US10030748B2 (en) | 2012-11-17 | 2018-07-24 | Dana Limited | Continuously variable transmission |
US9644530B2 (en) | 2013-02-08 | 2017-05-09 | Dana Limited | Internal combustion engine coupled turbocharger with an infinitely variable transmission |
US9404414B2 (en) | 2013-02-08 | 2016-08-02 | Dana Limited | Internal combustion engine coupled turbocharger with an infinitely variable transmission |
US8926468B2 (en) | 2013-03-14 | 2015-01-06 | Dana Limited | Ball type continuously variable transmission |
US9933054B2 (en) | 2013-03-14 | 2018-04-03 | Dana Limited | Continuously variable transmission and an infinitely variable transmission variator drive |
US9689482B2 (en) | 2013-03-14 | 2017-06-27 | Dana Limited | Ball type continuously variable transmission |
US20140274535A1 (en) * | 2013-03-14 | 2014-09-18 | Team Industries, Inc. | Continuously variable transmission with differential controlling assemblies |
US9194472B2 (en) | 2013-03-14 | 2015-11-24 | Dana Limited | Ball type continuously variable transmission |
US9551404B2 (en) | 2013-03-14 | 2017-01-24 | Dana Limited | Continuously variable transmission and an infinitely variable transmission variator drive |
US9638301B2 (en) | 2013-03-14 | 2017-05-02 | Dana Limited | Ball type continuously variable transmission |
US9133918B2 (en) * | 2013-03-14 | 2015-09-15 | Team Industries, Inc. | Continuously variable transmission with differential controlling assemblies |
US9677650B2 (en) | 2013-04-19 | 2017-06-13 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
US10323732B2 (en) | 2013-04-19 | 2019-06-18 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
WO2014179719A1 (en) * | 2013-05-03 | 2014-11-06 | Dana Limited | 4-mode rear wheel drive continuously variable planetary transmission |
US9777815B2 (en) | 2013-06-06 | 2017-10-03 | Dana Limited | 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission |
US10088022B2 (en) | 2013-11-18 | 2018-10-02 | Dana Limited | Torque peak detection and control mechanism for a CVP |
US10030751B2 (en) | 2013-11-18 | 2018-07-24 | Dana Limited | Infinite variable transmission with planetary gear set |
US10006529B2 (en) | 2014-06-17 | 2018-06-26 | Dana Limited | Off-highway continuously variable planetary-based multimode transmission including infinite variable transmission and direct continuously variable transmission |
US9382988B2 (en) * | 2014-10-17 | 2016-07-05 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
US9512911B2 (en) | 2014-10-17 | 2016-12-06 | Allison Transmission, Inc. | Split power continuously variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
WO2016061500A1 (en) * | 2014-10-17 | 2016-04-21 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low part count |
US9644721B2 (en) | 2014-10-17 | 2017-05-09 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges and low variator load at vehicle launch |
US9651127B2 (en) | 2014-10-17 | 2017-05-16 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low part count |
US9772017B2 (en) | 2014-10-17 | 2017-09-26 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low variator loading at vehicle launch |
EP3206903A4 (en) * | 2014-10-17 | 2018-07-04 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low part count |
US9644724B2 (en) | 2014-10-17 | 2017-05-09 | Allison Transmission, Inc. | Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges |
US10030594B2 (en) | 2015-09-18 | 2018-07-24 | Dana Limited | Abuse mode torque limiting control method for a ball-type continuously variable transmission |
US10920882B2 (en) | 2016-01-15 | 2021-02-16 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
US11306818B2 (en) | 2016-01-15 | 2022-04-19 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
US10047861B2 (en) | 2016-01-15 | 2018-08-14 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
US9970521B1 (en) * | 2016-02-26 | 2018-05-15 | Rodney J. Cook and successors in trust | Infinitely variable transmission |
US10458526B2 (en) | 2016-03-18 | 2019-10-29 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, systems and methods |
US11667351B2 (en) | 2016-05-11 | 2023-06-06 | Fallbrook Intellectual Property Company Llc | Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmission |
US10704662B2 (en) * | 2017-10-25 | 2020-07-07 | Zf Friedrichshafen Ag | Power-split continuously variable transmission device |
US11215268B2 (en) | 2018-11-06 | 2022-01-04 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same |
US11624432B2 (en) | 2018-11-06 | 2023-04-11 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same |
US11174922B2 (en) | 2019-02-26 | 2021-11-16 | Fallbrook Intellectual Property Company Llc | Reversible variable drives and systems and methods for control in forward and reverse directions |
US11530739B2 (en) | 2019-02-26 | 2022-12-20 | Fallbrook Intellectual Property Company Llc | Reversible variable drives and systems and methods for control in forward and reverse directions |
Also Published As
Publication number | Publication date |
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CN104121345A (en) | 2014-10-29 |
US9371894B2 (en) | 2016-06-21 |
US20130288848A1 (en) | 2013-10-31 |
CN101657653A (en) | 2010-02-24 |
US10260607B2 (en) | 2019-04-16 |
TWI548824B (en) | 2016-09-11 |
CN104121345B (en) | 2017-01-11 |
WO2008100792A1 (en) | 2008-08-21 |
CN101657653B (en) | 2014-07-16 |
US20160298740A1 (en) | 2016-10-13 |
TW200905106A (en) | 2009-02-01 |
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