US20060196457A1 - Valve actuator assembly - Google Patents
Valve actuator assembly Download PDFInfo
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- US20060196457A1 US20060196457A1 US11/367,968 US36796806A US2006196457A1 US 20060196457 A1 US20060196457 A1 US 20060196457A1 US 36796806 A US36796806 A US 36796806A US 2006196457 A1 US2006196457 A1 US 2006196457A1
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- Prior art keywords
- valve
- thrust
- plate
- actuator assembly
- valve actuator
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/042—Cam discs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
- F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L31/00—Valve drive, valve adjustment during operation, or other valve control, not provided for in groups F01L15/00 - F01L29/00
- F01L31/08—Valve drive or valve adjustment, apart from tripping aspects; Positively-driven gear
- F01L31/10—Valve drive or valve adjustment, apart from tripping aspects; Positively-driven gear the drive being effected by eccentrics
- F01L31/12—Valve adjustment by displacing eccentric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/181—Centre pivot rocking arms
- F01L1/182—Centre pivot rocking arms the rocking arm being pivoted about an individual fulcrum, i.e. not about a common shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/185—Overhead end-pivot rocking arms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/03—Auxiliary actuators
- F01L2820/032—Electric motors
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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
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/186—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions with reciprocation along the axis of oscillation
Definitions
- the present invention relates to a valve actuator assembly for controlling axial motion of a valve.
- FIG. 1 shows a typical type of prior art valve actuator with a cam lobe 1 acting directly upon a bucket lifter 2 which then transmits this motion to the valve 3 .
- FIG. 2 shows a typical type of prior art valve actuator with the cam lobe 1 acts upon a roller finger follower 2 A which pivots on a hydraulic lash adjuster 4 to open and close the valve 3 . It is often desirable to vary the timing of when the valve opens and the duration it remains open. These typical valve actuators make it difficult to control the timing and duration of the opening of the valve.
- a valve actuator assembly includes an axially movable valve in an internal combustion engine and a ramp roller thrust drive.
- the ramp roller thrust drive includes at least first and second opposed thrust plates, each plate including one or more ramps. At least one roller is positioned between corresponding opposed plate ramps, and a rotation of one of the thrust plates relative to the other thrust plate causes the plates to move axially relative to one another such that axial motion is imparted to the valve.
- a plate actuating mechanism is configured to rotate one of the plates relative to the other plate.
- a method for actuating an axially movable valve includes providing a ramp roller thrust drive including at least first and second opposed thrust plates, each plate including one or more ramps, and further including at least one roller positioned between corresponding opposed plate ramps. The method also includes rotating one of the thrust plates relative to the other thrust plate to impart axial motion to the valve.
- FIGS. 1 and 2 are side elevation schematic views of prior art valve actuators
- FIGS. 3 and 3 A are perspective, exploded views of roller ramp thrust drives of the present invention.
- FIGS. 4 and 5 are side elevation views of roller ramp thrust drives of the present invention.
- FIG. 6 is a side elevation view of a first embodiment of a valve ramp actuator assembly
- FIG. 6A is a side elevation view of a second embodiment of a valve ramp actuator assembly
- FIG. 7 is a side elevation view of a valve ramp actuator assembly along with an illustrative plate actuating mechanism
- FIG. 8 is a side elevation view of a valve ramp actuator assembly along with an alternative plate actuating mechanism
- FIGS. 9A-9C are a top plan view, a side cross sectional view and a graph, respectively, illustrating the valve lift in conjunction with a moderate oscillation angle
- FIGS. 10A-10C are a top plan view, a side cross sectional view and a graph, respectively, illustrating the valve lift in conjunction with a maximum oscillation angle
- FIGS. 11A-11C are a top plan view, a side cross sectional view and a graph, respectively, illustrating the valve lift in conjunction with a minimum oscillation angle
- FIG. 12 is a side elevation view of a third embodiment of a valve ramp actuator assembly
- FIG. 13 is a side elevation view of a fourth embodiment of a valve ramp actuator assembly.
- FIG. 14 is a side elevation view of a fifth embodiment of a valve ramp actuator assembly.
- a valve ramp actuator such as roller ramp thrust drive 45 is operable to convert rotary input motion into axial motion that is transmitted to a valve 3 (shown in FIGS. 6-8 and 12 - 14 ) in an internal combustion engine.
- Ramp thrust drive 45 includes a first plate 5 and a second plate 6 , each of which have one or more specially shaped, radially oriented recesses or ramps 7 which act as cam surfaces.
- Rollers 8 which can be cylindrical or tapered in shape, are placed in corresponding recesses and may be held in correct relative positions by a separator 9 .
- a central pin 10 is used to keep the plates 5 , 6 and separator 9 in the proper relationship to one another.
- FIG. 3A shows the use of a plurality of rollers 8 A with gear teeth 49 formed on the ends, which mesh with gear teeth 49 formed in the ramps 7 A, for example on the outer periphery of plates 5 A, 6 A.
- the gear teeth could also be formed elsewhere on the rollers and plates.
- FIG. 4 shows the operation of the roller ramp thrust drive 45 of FIG. 3 .
- a plate actuating mechanism 53 (such as that shown in FIGS. 7 and 8 ) provides relative rotative motion between the plates 5 , 6 .
- the plate 6 is stationary while plate 5 is rotated in the direction of the arrow.
- This action causes the rollers 8 to ride up the ramps 7 to cause an increase in the height H of the roller ramp thrust drive 45 .
- the ramps 7 can be shaped in such a way that a desired change in height is achieved for a given movement of a plate (or relative movement between plates).
- the distance D the plate 5 is moved is greater than the increase in height ⁇ H of thrust drive 45 .
- the result is a multiplication of the input force which is useful to overcome the forces holding a valve closed.
- FIG. 5 shows such a double ramp thrust drive 46 wherein an upper plate 14 and a lower plate 15 are stationary and a center plate 16 rotates relative to the upper and lower plates 14 , 15 .
- One benefit of the double ramp thrust drive 46 is that for a given amount of input movement and needed valve lift, the ramp angles can be made shallower to reduce contact stresses and improve the mechanical efficiency of the unit.
- FIG. 6 illustrates an embodiment of a valve ramp actuator assembly 48 including a double ramp thrust drive 46 that is used to actuate a valve 3 in an internal combustion engine.
- Valve 3 is axially movable between a closed position and an open position and can be an intake valve for allowing air to be drawn into a combustion chamber or an exhaust valve for allowing products of combustion to be removed from the combustion chamber.
- Valve 3 can be normally biased in a closed position by spring 51 having a spring retainer 37 .
- Guide 40 provides proper guidance for the axially movable valve 3 .
- FIG. 6 illustrates details of the spring retainer 37 and valve keeper 39 which is composed of two halves.
- the spring retainer 37 has been pushed downward, compressing the valve spring 51 .
- the upper end of valve stem 38 is meant to be positioned within a bore 42 in the plate 15 .
- a tapered inner diameter of retainer 37 engages the tapered outer diameters of the valve keeper 39 , forcing them inward to engage a groove 47 on the valve stem 38 .
- the valve 3 , retainer 37 and valve keeper 39 will be locked together and move as one unit if a force is applied to the upper end of the valve stem 38 via the movement of plate 15 .
- central pin 10 of FIG. 5 is not shown in FIG. 6 .
- the lower plate 15 acts directly on the valve 3 while the upper plate 14 reacts against a ground plane 17 connected to the primary structure of the engine.
- this ground plane 17 includes a hydraulic lash adjuster 18 which also helps insure proper seating of the valve 3 in the closed position.
- Input motion is applied to the center plate 16 .
- rotation of the upper plate 14 is prevented by a pin 19 which is fixed to the ground plane 17 .
- a slotted clip 20 is attached to the upper plate 14 and engages a pin 21 on the lower plate 15 to also prevent rotation of the lower plate 15 . Pin 21 can move axially as necessary in the slot of clip 20 .
- the timing of the valve opening can also be varied. As explained below, by altering the position of the clip 20 with respect to the plate 16 (and thus the ramps 7 ), the valve opening can occur at different times relative to a constant oscillating input motion.
- FIG. 6A illustrates an embodiment of a valve ramp actuator assembly 48 A including a double ramp thrust drive 46 A that is used to actuate valve 3 in an internal combustion engine.
- double roller ramp thrust drive 46 A includes anti-slipping gear teeth 49 on rollers 8 A and plates 14 A, 15 A, 16 A.
- FIG. 6A also illustrates valve 3 in a closed position.
- Input motion preferably oscillating input motion
- a plate in a variety of ways.
- input motion is provided to center plate 16 of double roller ramp thrust drive 46 by a plate actuating mechanism 53 .
- plate actuating mechanism includes an auxiliary rotating crankshaft 22 and connecting rod 23 which oscillates the center plate 16 through an oscillation angle 25 of the double roller ramp thrust drive 46 .
- Input motion can also be provided by a variety of other mechanical, hydraulic, electromechanical, electromagnetic, or similar devices.
- FIG. 8 shows the same ramp thrust drive 46 as in FIG. 7 , wherein plate actuating mechanism 53 provides oscillating input motion and includes a linear electromechanical actuator 27 .
- Actuators of this type can accurately control position, but are limited in their ability to control velocity.
- the double roller ramp thrust drive 46 provides the proper valve lift, velocity and acceleration for a given input displacement.
- the mechanical advantage provided by the double roller ramp thrust drive 46 means that a relatively low-power plate actuating mechanism 53 can be used to provide input motion to achieve a desired amount of valve lift.
- valve opening cycle For improve the efficiency and performance of an internal combustion engine, it is often desirable to alter the valve opening cycle for specific operating conditions. There are various ways to accomplish this. For example, with reference to FIG. 7 , altering the throw T of the crankshaft 22 will increase or decrease the oscillation angle 25 of the center plate 16 about a midpoint. This alters the amount of cam surface of the ramps 7 available to provide valve lift. In this same example, altering the length L of the connecting rod 23 will change the midpoint of the input oscillation towards one end of the cam surface or the other.
- An advantage of the thrust drive 46 is that the amount of valve lift for a given position of plate 16 is a direct function of the height of the cam surface or ramp 7 and an indirect function of the plate position. Having these two functions related, but separate, offers significant advantages in controlling valve motion.
- FIGS. 9A-9C , 10 A- 10 C, and 11 A- 11 C show how alterations in the oscillation angle and/or center point of rotation can use different parts of the cam surface for different operating conditions.
- FIGS. 9A-9C demonstrate a moderate oscillation angle 28 which results in roller movement over range 29 of the cam surface.
- the resulting valve lift 30 is sufficient to produce moderate engine power for normal operation.
- the oscillation angle 31 has been increased, resulting in roller movement over range 32 of the cam surface.
- the resulting valve lift 33 is both higher and broader, which can be used to allow an engine to develop maximum power.
- the oscillation angle 34 in FIGS. 11A-11C has been reduced and its midpoint shifted toward the flatter area of the cam surface. This results in roller movement over range 35 of the cam surface and minimal valve lift 36 , allowing an engine to operate with great efficiency under low load conditions such as idling.
- valve motion can be modified by changing the hydraulic characteristics of the lash adjuster 18 . Since the ramp thrust drive reacts against force of the lash adjuster 18 to open the valve 3 , a reduction in stiffness of this member will allow some of the increase in ramp thrust drive height to be absorbed as “lost motion” by the lash adjuster 18 . This can be accomplished by venting a portion of the fluid from a high pressure chamber of the lash adjuster 18 to a low pressure side for operating conditions that do not require full mechanical valve motion.
- An alternative to using the lash adjuster 18 to achieve modified valve motion would be to incorporate a position indicator and a feedback loop into the control system for the thrust drive 46 . Therefore, the hydraulic lash adjuster 18 need not be used in the illustrated valve actuator assemblies.
- FIG. 12 shows a cross section of a double roller ramp thrust drive 46 B not including the rollers 8 and ramps 7 .
- the lower plate 15 B of the drive 46 B is modified to include a valve spring seat 50 so that lower plate 15 B can function as the upper seat for valve spring 51 B.
- valve 3 B is modified by lengthening valve stem 38 B so that it extends into the ramp thrust drive 46 B, thereby eliminating the separate central pin 10 that is shown in FIGS. 3, 3A , and 5 .
- Two snap rings 44 engage grooves in the valve stem 38 B above and below plate 15 B. Elements 3 B, 15 B, and 44 then move as one unit against the valve spring 51 B, with the motion being provided by the axial movement of the ramp thrust drive 46 B.
- a central bore 54 in the middle plate 16 B allows for a slip fit on the valve stem 38 B, and relative movement between the middle plate 16 B and valve stem 38 B equal to half the valve lift.
- a central recess 55 in the upper plate 14 B provides a slip fit with the stem 38 B like the middle plate, however in this case the relative motion between the two is equal to the full extent of the valve lift. For this reason, it may be necessary to increase the thickness of the upper plate 14 B to have sufficient piloting length for the valve stem 38 B. Because the upper plate 14 B is stationary, this additional material is not detrimental to the performance of the valve assembly.
- valve guide 40 A distinct advantage of the arrangement illustrated in FIG. 12 concerns the guidance of the valve 3 B. In current internal combustion engines this function is accomplished entirely by the valve guide 40 .
- the valve stem 38 B is also guided in the upper plate 14 B which is biased, in this example, by the lash adjuster 18 .
- the fact that the valve is now guided in two places, and that these are widely separated, means that the alignment of the valve 3 B relative to its seat is significantly improved.
- the valve guide 40 can be made shorter or otherwise modified to reduce its size or improve the performance of the engine.
- FIG. 13 shows how the ramp thrust drive 46 can be used to replace the conventional cam lobe in the arrangement shown in FIG. 2 .
- the axial movement of the ramp thrust drive 46 causes a roller finger follower 52 , which pivots on hydraulic lash adjuster 18 A, to open and close the valve 3 .
- the roller finger follower 52 can be used to multiply the amount of lift created by the ramp thrust drive 46 .
- FIG. 14 shows another coupling mechanism that can multiply the lift generated by the ramp thrust drive 46 .
- a center pivot rocker arm 43 is used to perform this function.
- a lash adjuster 18 B can be used to compensate for excess clearance in the system.
Abstract
A valve actuator assembly includes an axially moveable valve and a ramp roller thrust drive. The ramp roller thrust drive includes at least first and second opposed thrust plates, each plate including one or more ramps. A roller is positioned between corresponding opposed plate ramps and a rotation of one of the thrust plates relative to the other thrust plate causes the plates to move axially relative to one another such that axial motion is imparted to the valve.
Description
- This application claims priority under 35 U.S.C. sec. 119 to provisional patent application No. 60/658,071, filed on Mar. 3, 2005, the entire contents of which is hereby incorporated by reference.
- The present invention relates to a valve actuator assembly for controlling axial motion of a valve.
- Typically valves in an internal combustion engine are opened and closed by the action of a camshaft lobe upon some type of valve lifter or rocker arm assembly.
FIG. 1 shows a typical type of prior art valve actuator with acam lobe 1 acting directly upon a bucket lifter 2 which then transmits this motion to thevalve 3. Another type of prior art valve actuator is shown inFIG. 2 , where thecam lobe 1 acts upon aroller finger follower 2A which pivots on a hydraulic lash adjuster 4 to open and close thevalve 3. It is often desirable to vary the timing of when the valve opens and the duration it remains open. These typical valve actuators make it difficult to control the timing and duration of the opening of the valve. - In one embodiment, a valve actuator assembly includes an axially movable valve in an internal combustion engine and a ramp roller thrust drive. The ramp roller thrust drive includes at least first and second opposed thrust plates, each plate including one or more ramps. At least one roller is positioned between corresponding opposed plate ramps, and a rotation of one of the thrust plates relative to the other thrust plate causes the plates to move axially relative to one another such that axial motion is imparted to the valve. A plate actuating mechanism is configured to rotate one of the plates relative to the other plate.
- A method for actuating an axially movable valve includes providing a ramp roller thrust drive including at least first and second opposed thrust plates, each plate including one or more ramps, and further including at least one roller positioned between corresponding opposed plate ramps. The method also includes rotating one of the thrust plates relative to the other thrust plate to impart axial motion to the valve.
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FIGS. 1 and 2 are side elevation schematic views of prior art valve actuators; -
FIGS. 3 and 3 A are perspective, exploded views of roller ramp thrust drives of the present invention; -
FIGS. 4 and 5 are side elevation views of roller ramp thrust drives of the present invention; -
FIG. 6 is a side elevation view of a first embodiment of a valve ramp actuator assembly; -
FIG. 6A is a side elevation view of a second embodiment of a valve ramp actuator assembly; -
FIG. 7 is a side elevation view of a valve ramp actuator assembly along with an illustrative plate actuating mechanism; -
FIG. 8 is a side elevation view of a valve ramp actuator assembly along with an alternative plate actuating mechanism; -
FIGS. 9A-9C are a top plan view, a side cross sectional view and a graph, respectively, illustrating the valve lift in conjunction with a moderate oscillation angle; -
FIGS. 10A-10C are a top plan view, a side cross sectional view and a graph, respectively, illustrating the valve lift in conjunction with a maximum oscillation angle; -
FIGS. 11A-11C are a top plan view, a side cross sectional view and a graph, respectively, illustrating the valve lift in conjunction with a minimum oscillation angle; -
FIG. 12 is a side elevation view of a third embodiment of a valve ramp actuator assembly; -
FIG. 13 is a side elevation view of a fourth embodiment of a valve ramp actuator assembly; and -
FIG. 14 is a side elevation view of a fifth embodiment of a valve ramp actuator assembly. - The present invention will be described with reference to the accompanying drawing figures wherein like numbers represent like elements throughout. Certain terminology, for example, “top”, “bottom”, “right”, “left”, “front”, “frontward”, “forward”, “back”, “rear” and “rearward”, is used in the following description for relative descriptive clarity only and is not intended to be limiting.
- Referring to
FIG. 3 , a valve ramp actuator such as rollerramp thrust drive 45 is operable to convert rotary input motion into axial motion that is transmitted to a valve 3 (shown inFIGS. 6-8 and 12-14) in an internal combustion engine.Ramp thrust drive 45 includes afirst plate 5 and asecond plate 6, each of which have one or more specially shaped, radially oriented recesses or ramps 7 which act as cam surfaces.Rollers 8, which can be cylindrical or tapered in shape, are placed in corresponding recesses and may be held in correct relative positions by aseparator 9. Acentral pin 10 is used to keep theplates separator 9 in the proper relationship to one another. - In order to prevent the
rollers 8 from moving out of position due to slipping on the ramps 7,FIG. 3A shows the use of a plurality ofrollers 8A withgear teeth 49 formed on the ends, which mesh withgear teeth 49 formed in theramps 7A, for example on the outer periphery ofplates 5A, 6A. The gear teeth could also be formed elsewhere on the rollers and plates. -
FIG. 4 shows the operation of the rollerramp thrust drive 45 ofFIG. 3 . A plate actuating mechanism 53 (such as that shown inFIGS. 7 and 8 ) provides relative rotative motion between theplates FIG. 4 theplate 6 is stationary whileplate 5 is rotated in the direction of the arrow. This action causes therollers 8 to ride up the ramps 7 to cause an increase in the height H of the rollerramp thrust drive 45. The ramps 7 can be shaped in such a way that a desired change in height is achieved for a given movement of a plate (or relative movement between plates). In general, the distance D theplate 5 is moved is greater than the increase in height ΔH ofthrust drive 45. The result is a multiplication of the input force which is useful to overcome the forces holding a valve closed. - In cases where a greater increase in height for a given input movement is necessary, it is possible to stack ramp thrust drives in series to multiply the effect. For example,
FIG. 5 shows such a doubleramp thrust drive 46 wherein anupper plate 14 and alower plate 15 are stationary and acenter plate 16 rotates relative to the upper andlower plates ramp thrust drive 46 is that for a given amount of input movement and needed valve lift, the ramp angles can be made shallower to reduce contact stresses and improve the mechanical efficiency of the unit. -
FIG. 6 illustrates an embodiment of a valveramp actuator assembly 48 including a doubleramp thrust drive 46 that is used to actuate avalve 3 in an internal combustion engine.Valve 3 is axially movable between a closed position and an open position and can be an intake valve for allowing air to be drawn into a combustion chamber or an exhaust valve for allowing products of combustion to be removed from the combustion chamber. Valve 3 can be normally biased in a closed position byspring 51 having aspring retainer 37.Guide 40 provides proper guidance for the axiallymovable valve 3. -
FIG. 6 illustrates details of thespring retainer 37 andvalve keeper 39 which is composed of two halves. InFIG. 6 , thespring retainer 37 has been pushed downward, compressing thevalve spring 51. Although not shown in the exploded view ofFIG. 6 , the upper end ofvalve stem 38 is meant to be positioned within abore 42 in theplate 15. A tapered inner diameter ofretainer 37 engages the tapered outer diameters of thevalve keeper 39, forcing them inward to engage agroove 47 on thevalve stem 38. When this occurs, thevalve 3,retainer 37 andvalve keeper 39 will be locked together and move as one unit if a force is applied to the upper end of thevalve stem 38 via the movement ofplate 15. Note that for simplification,central pin 10 ofFIG. 5 is not shown inFIG. 6 . - Thus, the
lower plate 15 acts directly on thevalve 3 while theupper plate 14 reacts against aground plane 17 connected to the primary structure of the engine. In the example shown, thisground plane 17 includes ahydraulic lash adjuster 18 which also helps insure proper seating of thevalve 3 in the closed position. Input motion is applied to thecenter plate 16. In this example, rotation of theupper plate 14 is prevented by apin 19 which is fixed to theground plane 17. A slottedclip 20 is attached to theupper plate 14 and engages apin 21 on thelower plate 15 to also prevent rotation of thelower plate 15.Pin 21 can move axially as necessary in the slot ofclip 20. Whenplate 16 is rotated relative to theother plates plates valve 3, thereby opening thevalve 3. - In some cases, the timing of the valve opening can also be varied. As explained below, by altering the position of the
clip 20 with respect to the plate 16 (and thus the ramps 7), the valve opening can occur at different times relative to a constant oscillating input motion. -
FIG. 6A illustrates an embodiment of a valveramp actuator assembly 48A including a double ramp thrust drive 46A that is used to actuatevalve 3 in an internal combustion engine. In this embodiment, double roller ramp thrust drive 46A includesanti-slipping gear teeth 49 onrollers 8A andplates 14A, 15A, 16A.FIG. 6A also illustratesvalve 3 in a closed position. - Input motion, preferably oscillating input motion, can be provided to a plate in a variety of ways. As illustrated in
FIG. 7 , input motion is provided to centerplate 16 of double roller ramp thrust drive 46 by aplate actuating mechanism 53. In this case, plate actuating mechanism includes an auxiliary rotating crankshaft 22 and connecting rod 23 which oscillates thecenter plate 16 through anoscillation angle 25 of the double rollerramp thrust drive 46. Input motion can also be provided by a variety of other mechanical, hydraulic, electromechanical, electromagnetic, or similar devices. - For example,
FIG. 8 shows the same ramp thrust drive 46 as inFIG. 7 , whereinplate actuating mechanism 53 provides oscillating input motion and includes a linear electromechanical actuator 27. Actuators of this type can accurately control position, but are limited in their ability to control velocity. The double roller ramp thrust drive 46 provides the proper valve lift, velocity and acceleration for a given input displacement. The mechanical advantage provided by the double roller ramp thrust drive 46 means that a relatively low-powerplate actuating mechanism 53 can be used to provide input motion to achieve a desired amount of valve lift. - To improve the efficiency and performance of an internal combustion engine, it is often desirable to alter the valve opening cycle for specific operating conditions. There are various ways to accomplish this. For example, with reference to
FIG. 7 , altering the throw T of the crankshaft 22 will increase or decrease theoscillation angle 25 of thecenter plate 16 about a midpoint. This alters the amount of cam surface of the ramps 7 available to provide valve lift. In this same example, altering the length L of the connecting rod 23 will change the midpoint of the input oscillation towards one end of the cam surface or the other. An advantage of thethrust drive 46 is that the amount of valve lift for a given position ofplate 16 is a direct function of the height of the cam surface or ramp 7 and an indirect function of the plate position. Having these two functions related, but separate, offers significant advantages in controlling valve motion. -
FIGS. 9A-9C , 10A-10C, and 11A-11C show how alterations in the oscillation angle and/or center point of rotation can use different parts of the cam surface for different operating conditions. For example,FIGS. 9A-9C demonstrate a moderate oscillation angle 28 which results in roller movement overrange 29 of the cam surface. The resultingvalve lift 30 is sufficient to produce moderate engine power for normal operation. InFIGS. 10A-10C , the oscillation angle 31 has been increased, resulting in roller movement overrange 32 of the cam surface. The resultingvalve lift 33 is both higher and broader, which can be used to allow an engine to develop maximum power. Theoscillation angle 34 inFIGS. 11A-11C has been reduced and its midpoint shifted toward the flatter area of the cam surface. This results in roller movement overrange 35 of the cam surface andminimal valve lift 36, allowing an engine to operate with great efficiency under low load conditions such as idling. - Another manner in which the valve motion can be modified is by changing the hydraulic characteristics of the
lash adjuster 18. Since the ramp thrust drive reacts against force of thelash adjuster 18 to open thevalve 3, a reduction in stiffness of this member will allow some of the increase in ramp thrust drive height to be absorbed as “lost motion” by thelash adjuster 18. This can be accomplished by venting a portion of the fluid from a high pressure chamber of thelash adjuster 18 to a low pressure side for operating conditions that do not require full mechanical valve motion. An alternative to using thelash adjuster 18 to achieve modified valve motion would be to incorporate a position indicator and a feedback loop into the control system for thethrust drive 46. Therefore, thehydraulic lash adjuster 18 need not be used in the illustrated valve actuator assemblies. - Another embodiment of a
valve actuator assembly 48B is shown inFIG. 12 , which shows a cross section of a double rollerramp thrust drive 46B not including therollers 8 and ramps 7. In this embodiment, thelower plate 15B of thedrive 46B is modified to include avalve spring seat 50 so thatlower plate 15B can function as the upper seat for valve spring 51B. This eliminates separatevalve spring retainer 37, such as is shown inFIG. 6 , and significantly reduces the reciprocating mass that must be accelerated as a function of opening the valve. This improves the performance and efficiency of thevalve actuator assembly 48B. - Further, the
valve 3B is modified by lengtheningvalve stem 38B so that it extends into theramp thrust drive 46B, thereby eliminating the separatecentral pin 10 that is shown inFIGS. 3, 3A , and 5. Two snap rings 44 engage grooves in the valve stem 38B above and belowplate 15B.Elements middle plate 16B allows for a slip fit on thevalve stem 38B, and relative movement between themiddle plate 16B and valve stem 38B equal to half the valve lift. A central recess 55 in theupper plate 14B provides a slip fit with thestem 38B like the middle plate, however in this case the relative motion between the two is equal to the full extent of the valve lift. For this reason, it may be necessary to increase the thickness of theupper plate 14B to have sufficient piloting length for thevalve stem 38B. Because theupper plate 14B is stationary, this additional material is not detrimental to the performance of the valve assembly. - A distinct advantage of the arrangement illustrated in
FIG. 12 concerns the guidance of thevalve 3B. In current internal combustion engines this function is accomplished entirely by thevalve guide 40. In this embodiment, thevalve stem 38B is also guided in theupper plate 14B which is biased, in this example, by thelash adjuster 18. The fact that the valve is now guided in two places, and that these are widely separated, means that the alignment of thevalve 3B relative to its seat is significantly improved. This also means that thevalve guide 40 can be made shorter or otherwise modified to reduce its size or improve the performance of the engine. - In addition to directly coupling the ramp thrust drive 46 and the
valve 3, various coupling mechanisms can be used instead. For example,FIG. 13 shows how the ramp thrust drive 46 can be used to replace the conventional cam lobe in the arrangement shown inFIG. 2 . The axial movement of the ramp thrust drive 46 causes aroller finger follower 52, which pivots onhydraulic lash adjuster 18A, to open and close thevalve 3. In this case, all of the advantages of the ramp thrust drive 46 still apply, however in this case theroller finger follower 52 can be used to multiply the amount of lift created by theramp thrust drive 46. -
FIG. 14 shows another coupling mechanism that can multiply the lift generated by theramp thrust drive 46. In this case a centerpivot rocker arm 43 is used to perform this function. A lash adjuster 18B can be used to compensate for excess clearance in the system.
Claims (20)
1. A valve actuator assembly comprising:
an axially movable valve; and
a ramp roller thrust drive including at least first and second opposed thrust plates, each plate including one or more ramps, and further including at least one roller positioned between corresponding opposed plate ramps, wherein a rotation of one of the thrust plates relative to the other thrust plate causes the plates to move axially relative to one another such that axial motion is imparted to the valve.
2. The valve actuator assembly of claim 1 , wherein the valve is in an internal combustion engine.
3. The valve actuator assembly of claim 1 , wherein the ramp roller thrust drive is a double roller thrust drive including a third stacked thrust plate.
4. The valve actuator assembly of claim 3 , wherein the center thrust plate is caused to rotate and the other two of the thrust plates are prevented from rotating.
5. The valve actuator assembly of claim 4 , wherein at least one of the stationary thrust plates is prevented from rotating using a slotted clip and a pin.
6. The valve actuator assembly of claim 1 , further including a lash adjuster for biasing the valve in a closed position.
7. The valve actuator assembly of claim 1 , further including a spring for biasing the valve in a closed position.
8. The valve actuator assembly of claim 7 , further including a valve keeper for coupling the spring to the valve.
9. The valve actuator assembly of claim 7 , wherein one of the thrust plates provides a seat for the spring.
10. The valve actuator assembly of claim 1 , wherein a valve stem of the valve extends axially through at least one thrust plate and keeps the plates in a proper relationship to one another.
11. The valve actuator assembly of claim 1 , further including at least one snap ring for coupling a movable plate to a valve stem of the valve.
12. The valve actuator assembly of claim 1 , further including a plate actuating mechanism configured to rotate one of the thrust plates relative to the other thrust plate.
13. The valve actuator assembly of claim 12 , wherein the plate actuating mechanism includes one of an electromagnetic actuator and an electromechanical actuator.
14. The valve actuator assembly of claim 12 , wherein the plate actuating mechanism is configured to provide oscillating motion to one of the thrust plates.
15. The valve actuator assembly of claim 12 , wherein the plate actuating mechanism includes a crankshaft and a connecting rod.
16. The valve actuator assembly of claim 1 , further including a coupling mechanism linking the ramp thrust drive and the valve, wherein the coupling mechanism multiplies an amount of axial movement of the ramp thrust drive which is imparted to the valve.
17. The valve actuator assembly of claim 16 , wherein the coupling mechanism includes one of a finger follower and a pivot rocker arm.
18. The valve actuator assembly of claim 1 , wherein the roller and the ramps include gear teeth.
19. A valve actuator assembly comprising:
a valve axially movable between a closed position for preventing a flow of gas to or from a combustion chamber of an internal combustion engine and an open position for allowing a flow of gas to or from the combustion chamber;
a ramp roller thrust drive including at least first and second opposed thrust plates, each plate including one or more ramps and including a corresponding roller positioned between opposed plate ramps such that rotation of one of the thrust plates relative to the other thrust plate causes the plates to move axially relative to one another such that axial motion is imparted to the valve; and
a plate actuating mechanism configured to provide oscillating rotative motion to one of the thrust plates relative to the other thrust plate.
20. A method for actuating an axially movable valve, the method comprising:
providing a ramp roller thrust drive including at least first and second opposed thrust plates, each plate including one or more ramps, and further including at least one roller positioned between corresponding opposed plate ramps; and
rotating one of the thrust plates relative to the other thrust plate to impart axial motion to the valve.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/367,968 US20060196457A1 (en) | 2005-03-03 | 2006-03-03 | Valve actuator assembly |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US65807105P | 2005-03-03 | 2005-03-03 | |
US11/367,968 US20060196457A1 (en) | 2005-03-03 | 2006-03-03 | Valve actuator assembly |
Publications (1)
Publication Number | Publication Date |
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US20060196457A1 true US20060196457A1 (en) | 2006-09-07 |
Family
ID=36617220
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US11/367,968 Abandoned US20060196457A1 (en) | 2005-03-03 | 2006-03-03 | Valve actuator assembly |
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US (1) | US20060196457A1 (en) |
WO (1) | WO2006094213A1 (en) |
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JP2018073963A (en) * | 2016-10-28 | 2018-05-10 | 新電元メカトロニクス株式会社 | Rotary solenoid |
US20200109648A1 (en) * | 2018-10-04 | 2020-04-09 | Jacobs Vehicle Systems, Inc. | Variable length piston assemblies for engine valve actuation systems |
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US11353084B2 (en) | 2013-03-15 | 2022-06-07 | Clearmotion Acquisition I Llc | Rotary actuator driven vibration isolation |
US9291300B2 (en) | 2013-03-15 | 2016-03-22 | Bose Corporation | Rotary actuator driven vibration isolation |
WO2014151845A1 (en) | 2013-03-15 | 2014-09-25 | Scuderi Group, Inc. | Split-cycle engines with direct injection |
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JP2018073963A (en) * | 2016-10-28 | 2018-05-10 | 新電元メカトロニクス株式会社 | Rotary solenoid |
US20200109648A1 (en) * | 2018-10-04 | 2020-04-09 | Jacobs Vehicle Systems, Inc. | Variable length piston assemblies for engine valve actuation systems |
WO2020072862A1 (en) * | 2018-10-04 | 2020-04-09 | Jacobs Vehicle Systems, Inc. | Variable length piston assemblies for engine valve actuation systems |
US10774693B2 (en) | 2018-10-04 | 2020-09-15 | Jacobs Vehicle Systems, Inc. | Variable length piston assemblies for engine valve actuation systems |
CN112789392A (en) * | 2018-10-04 | 2021-05-11 | 雅各布斯车辆系统公司 | Variable length piston assembly for engine valve actuation system |
KR20210058977A (en) * | 2018-10-04 | 2021-05-24 | 자콥스 비히클 시스템즈, 인코포레이티드. | Variable length piston assembly for engine valve actuation systems |
JP2022502602A (en) * | 2018-10-04 | 2022-01-11 | ジェイコブス ビークル システムズ、インコーポレイテッド | Variable length piston assembly for engine valve actuation system |
EP3861198A4 (en) * | 2018-10-04 | 2022-06-29 | Jacobs Vehicle Systems, Inc. | Variable length piston assemblies for engine valve actuation systems |
JP7383016B2 (en) | 2018-10-04 | 2023-11-17 | ジェイコブス ビークル システムズ、インコーポレイテッド | Variable length piston assembly for engine valve actuation systems |
KR102617301B1 (en) * | 2018-10-04 | 2023-12-21 | 자콥스 비히클 시스템즈, 인코포레이티드. | Variable length piston assemblies for engine valve actuation systems |
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