USRE33742E - Locking differential with electromagnetic actuated clutch - Google Patents
Locking differential with electromagnetic actuated clutch Download PDFInfo
- Publication number
- USRE33742E USRE33742E US07/608,001 US60800190A USRE33742E US RE33742 E USRE33742 E US RE33742E US 60800190 A US60800190 A US 60800190A US RE33742 E USRE33742 E US RE33742E
- Authority
- US
- United States
- Prior art keywords
- clutch
- cam
- case
- gear
- disks
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
-
- 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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
-
- 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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
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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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H2048/204—Control of arrangements for suppressing differential actions
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H2048/305—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using manual actuators
-
- 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
- F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
- F16H2048/346—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a linear motor
-
- 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
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/40—Constructional details characterised by features of the rotating cases
Definitions
- This invention relates to a limited slip differential mechanism for effectively transferring torque to both of a coaxially aligned pair of axles of a wheeled vehicle. More specifically it relates to a compact limited slip differential mechanism which includes an externally controllable electromagnetically operated clutch mechanism that provides a variable resistance to excessive relative rotation of the axles irrespective of the rate of relative rotation and of the output shaft torque level.
- the differential gear assembly disclosed herein is comprised of a gear driven differential case rotatably contained in a larger housing.
- a radially disposed planetary gear wheel is splined to one of a pair of coaxially aligned vehicle axles. It supports a plurality of pairs of meshed gears. One gear of each pair engages an annular gear formed on the inside of the differential case while the other gear of each pair engages a sun gear that is splined to the other axle.
- An electromagnetically operated clutch capable of being controlled from an external location is provided to limit relative rotation between the two axles. The level of resistance to relative rotation may be controlled irrespective of relative rotation.
- a cam operated supplemental clutch mechanism is incorporated in the clutch system to automatically apply additional side pressure against some of the clutch disks of the aforementioned clutch assembly in the event relative rotation continues after the electromagnet has been activated.
- the supplemental clutch mechanism is activated in part by the resistance resulting from the application of the first force and in part by any continuing differential rotation occurring during the duration of the first force.
- FIG. 1 is a sectional plan view of one embodiment of this invention taken along its centerline except for the planetary gear wheel assembly which is taken along line 1--1 FIG. 2,
- FIG. 2 is an enlarged right side view of the planetary gear wheel assembly of FIG. 1,
- FIG. 3 is a sectional plan view similar to FIG. 1 but of another embodiment of the invention.
- FIG. 4 is a partially sectioned view similar to FIG. 1 showing details of the supplemental clutch mechanism.
- FIG. 5 is an end view of an annular cam member of the supplemental clutch mechanism showing details of the cam teeth elements on its face.
- the differential gear assembly embodiment 10 illustrated in FIGS. 1 and 2 is comprised of an outer housing 12 containing a rotatable differential gear assembly case 14 mounted in a pair of coaxially disposed tapered roller bearings 16, 18 by means of hub sections 20, 22 extending from opposite ends of the case.
- the ends of coaxially aligned axles 24, 26 are journaled inside these hub sections.
- a pinion driven ring gear 28 is affixed to a radially disposed annular flange 30 on the periphery of the case.
- the case itself is made of two axially separable members 32, 34.
- the case member 32 on the left side of FIG. 1 has a large diameter circumferentially disposed annular gear 36 with inwardly facing parallel teeth integrally connected to the inside of the case member.
- a radially disposed planetary gear assembly 40 is mounted coaxially inside of the annular gear 36.
- the wheel has two parallel side plates 42, 44 the left one of which is integrally connected to the left side of hub section 46 which in turn is connected to the end of left axle 24 by means of internal splines.
- the circular central portion of the right plate 44 is cut out to form an annular opening between it and the periphery of the adjoining right end of the hub 46.
- the side plates have a plurality of parallel planar inner face sections. Meshed pairs of planet gears 48,50 are rotatably mounted on parallel pins 52 at the planar face sections.
- the side plates are cross connected by radially disposed web members 54 interposed between the pairs of planet gears. The thickness of the web members 54 increases in a radially inward direction.
- gear 48 One gear of each meshed pair, namely gear 48, is disposed closer to the periphery of the wheel than the other gear. These outer gears 48 all mesh with annular gear 36.
- the inner gear 50 of each pair is meshed with a sun gear 56 having a gear section which extends into the wheel through the annular opening in the right side plate 44.
- the sun gear 56 has a generally cylindrical midsection 58 which lies between an integrally connected left end section 60 and an integrally connected right end section 62.
- the right end section of the sun gear is splined internally to the end of the right axle 26 and extends between this axle and a concentric bearing surface 64 recessed in the end of the right case member 34.
- a radially disposed annular shoulder 66 which extends between the offset peripheries of the adjoining sections 58, 62 and bears against a corresponding annular shoulder on the right case member 34.
- the left end section 60 of the sun gear 56 is journaled on the planetary wheel hub 46 and thus is free to rotate about it.
- the radially disposed face 68 on the left end of section 60 bears against the inner wall of left side plate 42.
- the gear teeth on the outside of the sun gear 56 extend from its left end to the right end of its midsection 58.
- Clutch assembly 70 is incorporated in the differential to provide a variably controllable resistance to the relative rotation of the coaxially aligned output shafts of axles 24, 26.
- Clutch assembly 70 includes a wet clutch pack comprised of a plurality of laterally movable annular clutch disks concentrically stacked together side by side. Alternate disks 74 and intermediate disks 76 of the clutch pack are linked respectively by one or more components to the left and right axles 24, 26. For example, a plurality of intermediate clutch disks 76 are slidably keyed by mean of radially inwardly projecting teeth to the right end portion of the sun gear teeth surrounding its midsection 58. As was mentioned before, the sun gear 56 is splined to the right axle 26.
- the linkage or torque path between the alternate clutch disks 74 and axle 24 includes the right side case member 34, the left side case member 32, the annular gear 36 and the planetary wheel assembly 40.
- First of all the clutch disks 74 are slidably keyed to the right side case member 34.
- the number of alternate disks 74 linked to the left axle 24 exceeds the number of intermediate disks 76 linked to the right axle 76 by one.
- An axially movable clutch cage 78 having a radially disposed annular pressure plate 80 at one end, is used to apply a lateral force against an adjacent end face of the clutch pack which is sandwiched between the pressure plate 80 and an opposing annular clutch surface on the inside of case member 34.
- the clutch cage 78 has a plurality of parallel legs 82 which are integrally attached to the periphery of the pressure plate 80 and extend laterally to the right through apertures in the side wall of right side case member 34.
- An annular steel armature 84 spaced in close proximity to the outside surface of case member 34, is connected by threaded fasteners to the protruding ends of cage legs 82.
- An annular electromagnet 87 is mounted in a fixed portion inside of the differential housing 12 adjacent to the annular armature 84. It is symmetrically disposed with respect to the armature and the confronting face of these two components are spaced an effective distance from each other so that when the electromagnet is energized the armature and attached clutch cage will be drawn towards the electromagnet. This reaction compresses the clutch pack and increases the resistance to relative rotation between adjoining clutch disks 74, 76 and likewise between the components keyed to them. Activation of the electromagnet and regulation of the intensity of the magnetic field occur preferably by means of electronic controls or alternatively as a result of driver intervention. Electrical wires 88, 89 extend outwardly from the electromagnet 87 to an external control (not shown) which is accessible to the vehicle operator.
- the differential assembly embodiment 110 illustrated in this Fig. and the following Figs. is basically the same as the previously described embodiment 10 except for modifications relation to the inclusion of a cam operated supplemental clutch mechanism.
- the planetary wheel assembly 140 has been modified by the addition of an annular face cam member 141 integrally connected to the outside of right side plate 144 of assembly 140.
- a plurality of radially disposed truncated V-shaped cam elements in the form of grooves 143 are provided on the otherwise planar face of member 141.
- These cam grooves 143 are mated with an equal number of similarly shaped cam lobes or teeth 145 formed on the cam face end of a relatively rotatable annular cam collar member 147 (see FIG. 5).
- the cam slopes on opposite sides of each tooth are mirror images of one another.
- the effective angles of these cam slopes measured in a circumferential direction with respect to the adjoining planar face portion of member 147, decrease slightly in a radially outward direction.
- the mean angle of the slope is in the range from 20° to 30° and in the instant case is 25°.
- the slopes may be contoured or skewed so as to provide surface rather than line contact between the mating cam elements.
- Cam collar member 147 is mounted concentrically alongside cam element 141 and has a generally cylindrical body which extends axially from its cam face end to a clutch face end. It also has a plurality of rectangular grooves 149 formed in its periphery. These grooves extend from the clutch face end laterally towards the cam end of the body and are provided to slidably contain radially inwardly projecting clutch disk lugs of intermediate clutch disks 176'.
- the body of cam collar member 145 protrudes into the left end of the clutch pack through a first group of clutch disks comprising four alternate clutch disks 174' and three intermediate clutch disks 176'.
- Clutch disks 174' are slidably keyed to the right side case member 134 by radially outwardly extending lugs on their peripheries.
- the clutch face end of the cam body is adapted to bear against the left side of an intermediate clutch disk 176 which is the first disk of a second group of clutch pack disks.
- the second group is located on the right of the first group and includes alternate disks 174.
- Clutch disks 174, 176 are respectively linked to left and right axles 124, 126. It is to be noted that the electromagnetic clutch system operates directly on the clutch disks 174, 176, 174' 176' of both groups whereas the cam system operates directly on the clutch disks 174, 176 of the second group only.
- the annular electromagnet 187 in addition to being affixed to a rigid post of the outer housing 112 is supported on a plastic bushing 189 journaled on a cylindrical end of the right differential case section 134.
- the air gap between the face of the electromagnetic and the confronting face of the annular steel armature 184 is adjusted by means of annular shims 185 disposed between the left side of the bushing 189 and an opposing shoulder on the right side case member 134.
Abstract
Description
Claims (20)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US07/608,001 USRE33742E (en) | 1987-02-02 | 1990-11-01 | Locking differential with electromagnetic actuated clutch |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US07/009,831 US4781078A (en) | 1987-02-02 | 1987-02-02 | Locking differential with electromagnetic actuated clutch |
US07/608,001 USRE33742E (en) | 1987-02-02 | 1990-11-01 | Locking differential with electromagnetic actuated clutch |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US07/009,831 Reissue US4781078A (en) | 1987-02-02 | 1987-02-02 | Locking differential with electromagnetic actuated clutch |
Publications (1)
Publication Number | Publication Date |
---|---|
USRE33742E true USRE33742E (en) | 1991-11-12 |
Family
ID=26679918
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US07/608,001 Expired - Lifetime USRE33742E (en) | 1987-02-02 | 1990-11-01 | Locking differential with electromagnetic actuated clutch |
Country Status (1)
Country | Link |
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US (1) | USRE33742E (en) |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5269730A (en) * | 1990-06-05 | 1993-12-14 | Tochigifujisangyo Kabushiki Kaisha | Differential gear device for vehicle |
US6001040A (en) | 1998-02-25 | 1999-12-14 | Auburn Gear, Inc. | Hydraulically operated limited slip differential |
US6309320B1 (en) | 2000-01-18 | 2001-10-30 | Auburn Gear, Inc. | Direct housing mount of electromagnet |
US6544136B2 (en) | 2001-07-18 | 2003-04-08 | Visteon Global Technologies, Inc. | Differential device |
US6544137B2 (en) | 2001-07-18 | 2003-04-08 | Visteon Global Technologies, Inc. | Differential device |
US6575281B2 (en) | 2001-07-18 | 2003-06-10 | Visteon Global Technologies, Inc. | Coupling device |
US6591714B2 (en) | 2001-07-18 | 2003-07-15 | Visteon Global Technologies, Inc. | Coupling device |
US6676555B2 (en) | 2001-12-14 | 2004-01-13 | Visteon Global Technologies, Inc. | Cone friction clutch |
US6681913B2 (en) | 2001-07-18 | 2004-01-27 | Visteon Global Technologies, Inc. | Coupling device |
US20040024511A1 (en) * | 2000-10-11 | 2004-02-05 | Hyeongcheol Lee | Torque-biasing system |
US6859715B2 (en) | 2000-10-11 | 2005-02-22 | Visteon Global Technologies, Inc. | Torque-biasing system |
US20050090358A1 (en) * | 2003-10-27 | 2005-04-28 | Phelan Perry E. | Planetary differential |
US20080176702A1 (en) * | 2007-01-19 | 2008-07-24 | Showalter Dan J | Torque vectoring system |
US20090093334A1 (en) * | 2007-08-22 | 2009-04-09 | Orar Jacob Isaac-Lowry | Method and Kit to Convert an Open Differential to a Limited Slip Differential |
US20090112430A1 (en) * | 2005-08-16 | 2009-04-30 | Borgwarner Inc. | Electronic Control Torque Vectoring Axle |
US20090129560A1 (en) * | 2007-11-20 | 2009-05-21 | At&T Delaware Intellectual Property, Inc. | Methods, systems, and computer program products for managing traffic congestion in a network through detection of a source of excessive call volume |
US20180166235A1 (en) * | 2016-12-12 | 2018-06-14 | Logitech Europe S.A. | Input device including a ratchet system with an electromagnetic actuator |
Citations (34)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3323389A (en) * | 1964-11-30 | 1967-06-06 | Gen Motors Corp | Live axle |
US3419118A (en) * | 1966-12-01 | 1968-12-31 | Borg Warner | Electromagnetically actuated clutch |
US3448636A (en) * | 1967-05-09 | 1969-06-10 | Eaton Yale & Towne | Differential thrust mechanism |
GB1223435A (en) * | 1967-04-26 | 1971-02-24 | Jarmuefejlesztesi Intezet | Spur gear differential with automatic self-locking arrangement |
US3572165A (en) * | 1969-03-25 | 1971-03-23 | Eaton Yale & Towne | Clutch actuator for differential |
US3744609A (en) * | 1971-03-31 | 1973-07-10 | Bendix Corp | Self-adjusting two-way electromagnetic disc clutch |
US3789966A (en) * | 1971-03-31 | 1974-02-05 | Bendix Corp | Self-adjusting electromagnetic disc clutch |
US3818781A (en) * | 1973-01-02 | 1974-06-25 | Eaton Corp | Differential gear mechanism |
US3845671A (en) * | 1973-02-12 | 1974-11-05 | Chrysler Corp | Full time slip controlled four wheel drive |
US3869940A (en) * | 1972-01-07 | 1975-03-11 | Gkn Transmissions Ltd | Vehicle with differential assembly |
US3886813A (en) * | 1974-04-10 | 1975-06-03 | Eaton Corp | Differential |
US4022084A (en) * | 1974-05-09 | 1977-05-10 | Gkn Transmissions Limited | Control couplings |
US4030581A (en) * | 1975-08-25 | 1977-06-21 | Facet Enterprises, Inc. | Electromagnetic roller clutch |
US4031780A (en) * | 1974-11-29 | 1977-06-28 | Chrysler Corporation | Coupling apparatus for full time four wheel drive |
JPS5276568A (en) * | 1975-12-19 | 1977-06-28 | Aisin Seiki Co Ltd | Differential gear |
US4041804A (en) * | 1974-10-10 | 1977-08-16 | Caterpillar Tractor Co. | Limited slip differential with clutch control means |
US4048872A (en) * | 1974-05-28 | 1977-09-20 | Gkn Transmissions Limited | Control couplings |
US4059026A (en) * | 1974-11-04 | 1977-11-22 | The Gleason Works | Two stage limited slip differential |
DE2920107A1 (en) * | 1979-05-18 | 1980-11-20 | Bayerische Motoren Werke Ag | Differential gear for land vehicle - has output shafts lockable to stop differential operation by use of electrically-operated brake |
US4266445A (en) * | 1979-03-22 | 1981-05-12 | Eaton Corporation | Locking differential |
EP0032994A2 (en) * | 1979-12-26 | 1981-08-05 | Astro Development Corporation | Improved partially fluid-locked drive train |
US4290321A (en) * | 1979-06-25 | 1981-09-22 | Wilson Denney R | Variable lock differential |
JPS57178040A (en) * | 1981-04-24 | 1982-11-02 | Nippon Telegr & Teleph Corp <Ntt> | Excavator |
US4357840A (en) * | 1980-03-31 | 1982-11-09 | Caterpillar Tractor Co. | Multi-speed planetary differential |
US4389909A (en) * | 1981-05-26 | 1983-06-28 | Eaton Corporation | Cam mechanism for limited slip or locking differential |
US4400996A (en) * | 1980-03-04 | 1983-08-30 | Schou Carl Einar | Positive clutch differential |
US4412459A (en) * | 1981-04-15 | 1983-11-01 | Eaton Corporation | Controlled differential |
US4455596A (en) * | 1982-06-14 | 1984-06-19 | Ncr Corporation | Flyback-forward boost switchmode converter |
US4462272A (en) * | 1981-08-19 | 1984-07-31 | Rockwell International Corporation | Limited slip differential |
US4535651A (en) * | 1982-08-13 | 1985-08-20 | Caterpillar Tractor Co. | Torque proportioning differential |
US4554845A (en) * | 1982-10-01 | 1985-11-26 | Goscenski Jr Edward J | Positive drive and secondary clutch means therefor |
US4645049A (en) * | 1983-09-01 | 1987-02-24 | Honda Giken Kogyo Kabushiki Kaisha | Clutch system having means for converting transmitted torque into frictional force |
US4679463A (en) * | 1984-08-31 | 1987-07-14 | Nissan Motor Co., Ltd. | Limited slip differential |
GB2198493A (en) * | 1986-10-06 | 1988-06-15 | Borg Warner Automotive | Four wheel drive transfer case |
-
1990
- 1990-11-01 US US07/608,001 patent/USRE33742E/en not_active Expired - Lifetime
Patent Citations (35)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3323389A (en) * | 1964-11-30 | 1967-06-06 | Gen Motors Corp | Live axle |
US3419118A (en) * | 1966-12-01 | 1968-12-31 | Borg Warner | Electromagnetically actuated clutch |
GB1223435A (en) * | 1967-04-26 | 1971-02-24 | Jarmuefejlesztesi Intezet | Spur gear differential with automatic self-locking arrangement |
US3448636A (en) * | 1967-05-09 | 1969-06-10 | Eaton Yale & Towne | Differential thrust mechanism |
US3572165A (en) * | 1969-03-25 | 1971-03-23 | Eaton Yale & Towne | Clutch actuator for differential |
US3744609A (en) * | 1971-03-31 | 1973-07-10 | Bendix Corp | Self-adjusting two-way electromagnetic disc clutch |
US3789966A (en) * | 1971-03-31 | 1974-02-05 | Bendix Corp | Self-adjusting electromagnetic disc clutch |
US3869940A (en) * | 1972-01-07 | 1975-03-11 | Gkn Transmissions Ltd | Vehicle with differential assembly |
US3818781A (en) * | 1973-01-02 | 1974-06-25 | Eaton Corp | Differential gear mechanism |
US3845671A (en) * | 1973-02-12 | 1974-11-05 | Chrysler Corp | Full time slip controlled four wheel drive |
US3886813A (en) * | 1974-04-10 | 1975-06-03 | Eaton Corp | Differential |
US4022084A (en) * | 1974-05-09 | 1977-05-10 | Gkn Transmissions Limited | Control couplings |
US4048872A (en) * | 1974-05-28 | 1977-09-20 | Gkn Transmissions Limited | Control couplings |
US4041804A (en) * | 1974-10-10 | 1977-08-16 | Caterpillar Tractor Co. | Limited slip differential with clutch control means |
US4059026A (en) * | 1974-11-04 | 1977-11-22 | The Gleason Works | Two stage limited slip differential |
US4031780A (en) * | 1974-11-29 | 1977-06-28 | Chrysler Corporation | Coupling apparatus for full time four wheel drive |
US4030581A (en) * | 1975-08-25 | 1977-06-21 | Facet Enterprises, Inc. | Electromagnetic roller clutch |
JPS5276568A (en) * | 1975-12-19 | 1977-06-28 | Aisin Seiki Co Ltd | Differential gear |
US4266445A (en) * | 1979-03-22 | 1981-05-12 | Eaton Corporation | Locking differential |
DE2920107A1 (en) * | 1979-05-18 | 1980-11-20 | Bayerische Motoren Werke Ag | Differential gear for land vehicle - has output shafts lockable to stop differential operation by use of electrically-operated brake |
US4290321A (en) * | 1979-06-25 | 1981-09-22 | Wilson Denney R | Variable lock differential |
US4389908A (en) * | 1979-12-26 | 1983-06-28 | Astro Development Corporation | Partially fluid locked drive train |
EP0032994A2 (en) * | 1979-12-26 | 1981-08-05 | Astro Development Corporation | Improved partially fluid-locked drive train |
US4400996A (en) * | 1980-03-04 | 1983-08-30 | Schou Carl Einar | Positive clutch differential |
US4357840A (en) * | 1980-03-31 | 1982-11-09 | Caterpillar Tractor Co. | Multi-speed planetary differential |
US4412459A (en) * | 1981-04-15 | 1983-11-01 | Eaton Corporation | Controlled differential |
JPS57178040A (en) * | 1981-04-24 | 1982-11-02 | Nippon Telegr & Teleph Corp <Ntt> | Excavator |
US4389909A (en) * | 1981-05-26 | 1983-06-28 | Eaton Corporation | Cam mechanism for limited slip or locking differential |
US4462272A (en) * | 1981-08-19 | 1984-07-31 | Rockwell International Corporation | Limited slip differential |
US4455596A (en) * | 1982-06-14 | 1984-06-19 | Ncr Corporation | Flyback-forward boost switchmode converter |
US4535651A (en) * | 1982-08-13 | 1985-08-20 | Caterpillar Tractor Co. | Torque proportioning differential |
US4554845A (en) * | 1982-10-01 | 1985-11-26 | Goscenski Jr Edward J | Positive drive and secondary clutch means therefor |
US4645049A (en) * | 1983-09-01 | 1987-02-24 | Honda Giken Kogyo Kabushiki Kaisha | Clutch system having means for converting transmitted torque into frictional force |
US4679463A (en) * | 1984-08-31 | 1987-07-14 | Nissan Motor Co., Ltd. | Limited slip differential |
GB2198493A (en) * | 1986-10-06 | 1988-06-15 | Borg Warner Automotive | Four wheel drive transfer case |
Cited By (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5269730A (en) * | 1990-06-05 | 1993-12-14 | Tochigifujisangyo Kabushiki Kaisha | Differential gear device for vehicle |
US6001040A (en) | 1998-02-25 | 1999-12-14 | Auburn Gear, Inc. | Hydraulically operated limited slip differential |
US6309320B1 (en) | 2000-01-18 | 2001-10-30 | Auburn Gear, Inc. | Direct housing mount of electromagnet |
US20040024511A1 (en) * | 2000-10-11 | 2004-02-05 | Hyeongcheol Lee | Torque-biasing system |
US6882922B2 (en) | 2000-10-11 | 2005-04-19 | Visteon Global Technologies, Inc. | Torque-biasing system |
US6859715B2 (en) | 2000-10-11 | 2005-02-22 | Visteon Global Technologies, Inc. | Torque-biasing system |
US6575281B2 (en) | 2001-07-18 | 2003-06-10 | Visteon Global Technologies, Inc. | Coupling device |
US6681913B2 (en) | 2001-07-18 | 2004-01-27 | Visteon Global Technologies, Inc. | Coupling device |
US6591714B2 (en) | 2001-07-18 | 2003-07-15 | Visteon Global Technologies, Inc. | Coupling device |
US6544137B2 (en) | 2001-07-18 | 2003-04-08 | Visteon Global Technologies, Inc. | Differential device |
US6544136B2 (en) | 2001-07-18 | 2003-04-08 | Visteon Global Technologies, Inc. | Differential device |
US6676555B2 (en) | 2001-12-14 | 2004-01-13 | Visteon Global Technologies, Inc. | Cone friction clutch |
US7008345B2 (en) * | 2003-10-27 | 2006-03-07 | Automotive Components Holdings Inc. | Planetary differential |
US20050090358A1 (en) * | 2003-10-27 | 2005-04-28 | Phelan Perry E. | Planetary differential |
US20090112430A1 (en) * | 2005-08-16 | 2009-04-30 | Borgwarner Inc. | Electronic Control Torque Vectoring Axle |
US8083636B2 (en) | 2005-08-16 | 2011-12-27 | Borgwarner, Inc. | Electronic control torque vectoring axle |
US20080176702A1 (en) * | 2007-01-19 | 2008-07-24 | Showalter Dan J | Torque vectoring system |
US20090093334A1 (en) * | 2007-08-22 | 2009-04-09 | Orar Jacob Isaac-Lowry | Method and Kit to Convert an Open Differential to a Limited Slip Differential |
US20090129560A1 (en) * | 2007-11-20 | 2009-05-21 | At&T Delaware Intellectual Property, Inc. | Methods, systems, and computer program products for managing traffic congestion in a network through detection of a source of excessive call volume |
US8135116B2 (en) | 2007-11-20 | 2012-03-13 | At&T Intellectual Property I, L.P. | Methods, systems, and computer program products for managing traffic congestion in a network through detection of a source of excessive call volume |
US20180166235A1 (en) * | 2016-12-12 | 2018-06-14 | Logitech Europe S.A. | Input device including a ratchet system with an electromagnetic actuator |
US10642467B2 (en) * | 2016-12-12 | 2020-05-05 | Logitech Europe S.A. | Input device including a ratchet system with an electromagnetic actuator |
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