US20040099500A1 - Torque-transmitting torque to thrust apply mechanism having amplified thrust - Google Patents
Torque-transmitting torque to thrust apply mechanism having amplified thrust Download PDFInfo
- Publication number
- US20040099500A1 US20040099500A1 US10/303,530 US30353002A US2004099500A1 US 20040099500 A1 US20040099500 A1 US 20040099500A1 US 30353002 A US30353002 A US 30353002A US 2004099500 A1 US2004099500 A1 US 2004099500A1
- Authority
- US
- United States
- Prior art keywords
- apply
- torque
- thrust
- ramp surface
- axially displacing
- 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.)
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Classifications
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/04—Friction clutches with means for actuating or keeping engaged by a force derived at least partially from one of the shafts to be connected
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
- F16D27/004—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with permanent magnets combined with electromagnets
Definitions
- This invention relates to torque-transmitting apply mechanisms and, more particularly, to thrust apply mechanisms incorporating ball ramp mechanisms.
- a majority of prior art torque-transmitting mechanisms employ hydraulic apply systems wherein a fluid-operated piston is pressurized with hydraulic fluid to apply axial thrust to a plurality of friction discs thereby transmitting torque between two members of the torque-transmitting mechanism.
- These hydraulic systems require fluid passages to be formed in the transmission housing and requires a somewhat complicated valving mechanism to ensure the proper interaction of the hydraulic fluid with the devices to be controlled.
- an electric motor torque is converted to an axial thrust, in a torque to thrust mechanism which in turn applies engagement force to a torque-transmitting mechanism.
- an electric motor supplies rotary torque to a ball and ramp system, which converts the rotary torque to an axial thrust force.
- the axial thrust force of the ball ramp system is initiated by a first ball ramp mechanism forcing frictional engagement between friction plates of a torque-transmitting mechanism.
- axial movement of the initiating ball ramp also results in rotary movement of a second ball ramp, which in turn produces additional thrust on the torque-transmitting mechanisms to provide full engagement of the torque-transmitting mechanism.
- FIG. 1 is a cross-sectional elevational view of a torque-transmitting mechanism, incorporating the present invention within a power transmission.
- FIG. 2 is a block diagram representation of a portion of the torque-transmitting apply mechanism shown in FIG. 1.
- FIG. 3 is a block diagram representation of an alternative embodiment of the thrust mechanism shown in FIG. 2.
- FIG. 1 a torque-transmitting mechanism, generally designated 10 , which is a component of a power transmission, not shown.
- the torque-transmitting mechanism 10 includes a stationary housing portion 12 , a rotating hub portion 14 , a first plurality of friction plates or discs 16 , and a second plurality of friction plates or discs 18 .
- the friction plates 18 are interdicted with the friction plates 16 .
- the friction plates 16 are splined to the stationary housing 12 and limited in rightward movement, as seen in FIG. 1, by a conventional locking ring 20 .
- the friction discs 18 are splined to the hub 14 and are free to move axially thereon between the friction plates 16 .
- the torque-transmitting mechanism 10 also includes a first annular apply plate 22 and a second annular apply plate 24 .
- the annular apply plate 24 is splined to the annular apply plate 22 at 26 wherein a spline 28 is formed on the apply plate 22 and a spline 30 is formed on the apply plate 24 .
- the apply plate 22 is rotatably supported on an input member 32 , which is in turn rotatably supported on a plurality of needle bearings 34 and also supported by a thrust bearing 36 .
- the apply plate 22 and input member 32 are separated by a plurality of balls or spheres or cylindrical rollers 38 .
- the input member 32 has splined on the outer periphery thereof a gear 40 which meshes with a gear 42 which in turn is rotatably driven by an electric motor 44 .
- the input member 32 has formed thereon an axially displacing annular ramp face 46 and the apply member 22 has formed thereon a flat side face 48 .
- the balls or spheres or cylindrical rollers 38 abut the faces 46 and 48 .
- the input member 32 A has an axially displacing annular ramp face 46 A and the apply plate 22 A has a flat side face 48 A.
- the apply plate 24 has an axial ramp surface 50 and the housing 12 has formed thereon an axial surface or reaction member 52 . These surfaces and 50 and 52 are separated by a plurality of spheres or balls or cylindrical rollers 54 .
- the surface 52 A of the housing 12 is a flat surface and the surface 50 A of the apply plate 24 A is an axially displacing annular ramp surface.
- the apply plate 24 also has a second axial surface 56 , which is separated from the friction plates 16 by a thrust bearing 58 .
- the apply plate 24 is capable of applying thrust to the plates 16 while relative rotation therebetween is permitted, and the surface 52 is a reaction surface or member.
- the input member 32 When the electric motor 44 is rotated, the input member 32 will also rotate through the gear mesh resulting in further movement of the input member 32 in the direction of Arrow A, as seen in FIG. 2. As the input member 32 A rotates in the direction of Arrow A, the spheres 34 A will move axially toward the apply plate 22 A because of the ramp surface 46 A. This will result in axial movement of the apply plate 22 A toward the friction plates 18 . As the friction plates 18 come into abutment with the friction plates 16 , a rotary force in the direction of Arrow B will be imposed upon the apply plate 22 due the rotation of the hub 14 . The rotation of the apply plate 22 will be transmitted to the apply plate 24 such that the apply plate 24 will be rotated in the direction of Arrow C.
- the torque-transmitting mechanism 10 might be employed for two different ratios, for example, an underdrive forward speed ratio and an overdrive forward speed ratio.
- the reaction torque on the hub 14 would be in a direction opposite to the torque during the underdrive ratio.
- the reaction force is considerably less during the overdrive ratio and therefore the electric motor 44 has sufficient torque capability to maintain the torque-transmitting mechanism 10 fully engaged during the reverse torque operation.
- FIG. 3 An alternative embodiment, shown in FIG. 3,. describes the input member 32 B as having an annular ramp face 46 B and the apply plate 22 B having an angular ramp face 48 B.
- the rotary movement of the input member 32 B in the direction of Arrow C will result in further axial movement of the apply plate 22 B in the direction of Arrow D thereby shortening the amount of rotation of the electric motor 44 to initiate application of the torque-transmitting mechanism 10 .
- housing 12 B has an axially displacing annular ramp surface 52 B instead of a flat face as shown as 52 A in FIG. 2.
- the apply plate 24 B also has an axially displacing annular ramp surface 50 B.
- the apply plate 24 B will be axially moved in the direction of Arrow H as a result of the interaction between the balls 54 B and the ramps 52 B and 50 B.
- the axial movement of the apply plate 24 B will be further for a given amount of rotation than the axial thrust or axial movement of the plate 24 A. Again, the apply time for the full engagement of the torque-transmitting mechanism 10 is reduced.
- the electric motor 44 supplies sufficient torque to initiate axial thrust of the apply plate 22 and initial engagement of the friction plates 18 and 16 .
- the rotation of the hub 14 which is a result of torque reaction, will cause rotation of the apply plate 22 .
- the rotation of the apply plate 22 is transmitted to the apply plate 24 which will therefore rotate in unison with the apply plate 22 .
- the rotation of the apply plate 24 results in additional thrust on the friction plates 16 and 18 such that the torque of the electric motor 44 is amplified by the reaction torque of the torque-transmitting mechanism 10 . This, of course, reduces the necessary size and torque output of the electric motor 44 thereby reducing the overall size and weight of the control mechanism.
- the gears 40 and 42 are depicted as third gears or helical gears. It is also possible to use other types of gear engagement mechanisms such as converting the gear 40 to a worm gear and the gear 42 to a worm in which case the motor in gear 42 could be displaced ninety degrees to the mechanism shown FIG. 1. These types of gear arrangements are well known to those skilled in the art and can be interchanged with no conflict in the design or operation of the system.
- the present invention represents an improved torque-to-thrust apply mechanism for torque-transmitting mechanisms.
- the torque is presented in a form of rotary motion from an electric motor and the thrust is a result of this torque being transmitted through a plurality of ramp mechanisms to a thrust force, which is utilized to provide the engagement force within the torque-transmitting mechanism.
- the above-described system employs spheres, which cooperate with ramp portions to convert the torque input to a thrust output.
- Other mechanisms for converting the torque-to-thrust might be employed such as lead screws or spiral springs to name a few of the conversion mechanisms to be employed.
- the preferable roller mechanism is in the form of spheres such as those shown with the embodiment of the present invention. However, those skilled in the art will recognize that other mechanisms are employable within the confines of the present invention.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
Description
- This invention relates to torque-transmitting apply mechanisms and, more particularly, to thrust apply mechanisms incorporating ball ramp mechanisms.
- A majority of prior art torque-transmitting mechanisms employ hydraulic apply systems wherein a fluid-operated piston is pressurized with hydraulic fluid to apply axial thrust to a plurality of friction discs thereby transmitting torque between two members of the torque-transmitting mechanism. These hydraulic systems require fluid passages to be formed in the transmission housing and requires a somewhat complicated valving mechanism to ensure the proper interaction of the hydraulic fluid with the devices to be controlled.
- More recently, electromagnetic apply clutches have been suggested and viscous clutches have also been employed. A more recent event is the introduction of ball ramp or roller ramp apply mechanisms, which convert electric motor torque to axial thrust to establish the frictional engagement between adjacent torque-transmitting friction plates.
- It is an object of the present invention to provide an improved torque-transmitting engagement mechanism.
- In one aspect of the present invention, an electric motor torque is converted to an axial thrust, in a torque to thrust mechanism which in turn applies engagement force to a torque-transmitting mechanism.
- In another aspect of the present invention, an electric motor supplies rotary torque to a ball and ramp system, which converts the rotary torque to an axial thrust force.
- In yet another aspect of the present invention, the axial thrust force of the ball ramp system is initiated by a first ball ramp mechanism forcing frictional engagement between friction plates of a torque-transmitting mechanism.
- In yet still another aspect of the present invention, axial movement of the initiating ball ramp also results in rotary movement of a second ball ramp, which in turn produces additional thrust on the torque-transmitting mechanisms to provide full engagement of the torque-transmitting mechanism.
- FIG. 1 is a cross-sectional elevational view of a torque-transmitting mechanism, incorporating the present invention within a power transmission.
- FIG. 2 is a block diagram representation of a portion of the torque-transmitting apply mechanism shown in FIG. 1.
- FIG. 3 is a block diagram representation of an alternative embodiment of the thrust mechanism shown in FIG. 2.
- Referring to the drawings, wherein like characters represent the same or corresponding parts throughout the several views, there is seen in FIG. 1 a torque-transmitting mechanism, generally designated10, which is a component of a power transmission, not shown. The torque-
transmitting mechanism 10 includes astationary housing portion 12, arotating hub portion 14, a first plurality of friction plates ordiscs 16, and a second plurality of friction plates ordiscs 18. Thefriction plates 18 are interdicted with thefriction plates 16. Thefriction plates 16 are splined to thestationary housing 12 and limited in rightward movement, as seen in FIG. 1, by aconventional locking ring 20. Thefriction discs 18 are splined to thehub 14 and are free to move axially thereon between thefriction plates 16. - The torque-
transmitting mechanism 10 also includes a firstannular apply plate 22 and a secondannular apply plate 24. Theannular apply plate 24 is splined to theannular apply plate 22 at 26 wherein aspline 28 is formed on the applyplate 22 and aspline 30 is formed on the applyplate 24. The applyplate 22 is rotatably supported on aninput member 32, which is in turn rotatably supported on a plurality ofneedle bearings 34 and also supported by a thrust bearing 36. - The apply
plate 22 andinput member 32 are separated by a plurality of balls or spheres orcylindrical rollers 38. Theinput member 32 has splined on the outer periphery thereof agear 40 which meshes with agear 42 which in turn is rotatably driven by anelectric motor 44. Theinput member 32 has formed thereon an axially displacingannular ramp face 46 and the applymember 22 has formed thereon aflat side face 48. The balls or spheres orcylindrical rollers 38 abut thefaces - As seen in FIG. 2, the
input member 32A has an axially displacingannular ramp face 46A and the applyplate 22A has a flat side face 48A. The applyplate 24 has anaxial ramp surface 50 and thehousing 12 has formed thereon an axial surface orreaction member 52. These surfaces and 50 and 52 are separated by a plurality of spheres or balls orcylindrical rollers 54. As seen in FIG. 2, thesurface 52A of thehousing 12 is a flat surface and thesurface 50A of the applyplate 24A is an axially displacing annular ramp surface. The applyplate 24 also has a secondaxial surface 56, which is separated from thefriction plates 16 by a thrust bearing 58. Thus, the applyplate 24 is capable of applying thrust to theplates 16 while relative rotation therebetween is permitted, and thesurface 52 is a reaction surface or member. - When the
electric motor 44 is rotated, theinput member 32 will also rotate through the gear mesh resulting in further movement of theinput member 32 in the direction of Arrow A, as seen in FIG. 2. As theinput member 32A rotates in the direction of Arrow A, thespheres 34A will move axially toward the applyplate 22A because of theramp surface 46A. This will result in axial movement of the applyplate 22A toward thefriction plates 18. As thefriction plates 18 come into abutment with thefriction plates 16, a rotary force in the direction of Arrow B will be imposed upon the applyplate 22 due the rotation of thehub 14. The rotation of the applyplate 22 will be transmitted to the applyplate 24 such that the applyplate 24 will be rotated in the direction of Arrow C. - Due to the
ramp surface 50 on applyplate 24 and thespheres 54, the applyplate 24 will be moved axially toward thefriction discs 16 to apply additional thrust to thefriction plates transmitting mechanism 10 is fully engaged, the relative rotation ofdiscs 18 anddiscs 16 will cease and both plates will be held stationary or rotate in unison depending upon the type torque-transmitting mechanism. At this point, the maximum torque-to-thrust phenomenon will be completed and the torque-transmittingmechanism 10 is, as stated above, fully engaged. - There are instances under which the torque on the torque-
transmitting mechanism 10 will be reversed, which would normally tend to disengage the torque-transmitting mechanism through the ramp applied. However, as long as theelectric motor 44 maintains at least one-third to one-half the required thrust on the torque transmitting mechanism, there will be sufficient thrust applied to maintain the torque-transmittingmechanism 10 fully engaged during the coast operation. - In some transmissions, the torque-
transmitting mechanism 10 might be employed for two different ratios, for example, an underdrive forward speed ratio and an overdrive forward speed ratio. During the overdrive forward speed ratio, the reaction torque on thehub 14 would be in a direction opposite to the torque during the underdrive ratio. However, the reaction force is considerably less during the overdrive ratio and therefore theelectric motor 44 has sufficient torque capability to maintain the torque-transmittingmechanism 10 fully engaged during the reverse torque operation. - An alternative embodiment, shown in FIG. 3,. describes the
input member 32B as having anannular ramp face 46B and the applyplate 22B having anangular ramp face 48B. In this arrangement, the rotary movement of theinput member 32B in the direction of Arrow C will result in further axial movement of the applyplate 22B in the direction of Arrow D thereby shortening the amount of rotation of theelectric motor 44 to initiate application of the torque-transmitting mechanism 10. - Also shown in FIG. 3,
housing 12B has an axially displacingannular ramp surface 52B instead of a flat face as shown as 52A in FIG. 2. The applyplate 24B also has an axially displacingannular ramp surface 50B. As the applyplate 24B is rotated in the direction of Arrow F, which is a result of the rotation of the applyplate 22B in the direction of Arrow G, the applyplate 24B will be axially moved in the direction of Arrow H as a result of the interaction between theballs 54B and theramps plate 24B will be further for a given amount of rotation than the axial thrust or axial movement of theplate 24A. Again, the apply time for the full engagement of the torque-transmitting mechanism 10 is reduced. - With the present invention, the
electric motor 44 supplies sufficient torque to initiate axial thrust of the applyplate 22 and initial engagement of thefriction plates friction plates hub 14, which is a result of torque reaction, will cause rotation of theapply plate 22. The rotation of the applyplate 22 is transmitted to the applyplate 24 which will therefore rotate in unison with theapply plate 22. The rotation of the applyplate 24 results in additional thrust on thefriction plates electric motor 44 is amplified by the reaction torque of the torque-transmitting mechanism 10. This, of course, reduces the necessary size and torque output of theelectric motor 44 thereby reducing the overall size and weight of the control mechanism. - The
gears gear 40 to a worm gear and thegear 42 to a worm in which case the motor ingear 42 could be displaced ninety degrees to the mechanism shown FIG. 1. These types of gear arrangements are well known to those skilled in the art and can be interchanged with no conflict in the design or operation of the system. - The present invention represents an improved torque-to-thrust apply mechanism for torque-transmitting mechanisms. The torque is presented in a form of rotary motion from an electric motor and the thrust is a result of this torque being transmitted through a plurality of ramp mechanisms to a thrust force, which is utilized to provide the engagement force within the torque-transmitting mechanism.
- The above-described system employs spheres, which cooperate with ramp portions to convert the torque input to a thrust output. Other mechanisms for converting the torque-to-thrust might be employed such as lead screws or spiral springs to name a few of the conversion mechanisms to be employed. The preferable roller mechanism is in the form of spheres such as those shown with the embodiment of the present invention. However, those skilled in the art will recognize that other mechanisms are employable within the confines of the present invention.
Claims (5)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/303,530 US6742642B1 (en) | 2002-11-25 | 2002-11-25 | Torque-transmitting torque to thrust apply mechanism having amplified thrust |
DE10355071A DE10355071B4 (en) | 2002-11-25 | 2003-11-25 | Torque transmitting actuator mechanism with transfer of torque to boosted thrust |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US10/303,530 US6742642B1 (en) | 2002-11-25 | 2002-11-25 | Torque-transmitting torque to thrust apply mechanism having amplified thrust |
Publications (2)
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US20040099500A1 true US20040099500A1 (en) | 2004-05-27 |
US6742642B1 US6742642B1 (en) | 2004-06-01 |
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US10/303,530 Expired - Fee Related US6742642B1 (en) | 2002-11-25 | 2002-11-25 | Torque-transmitting torque to thrust apply mechanism having amplified thrust |
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US (1) | US6742642B1 (en) |
DE (1) | DE10355071B4 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2005119076A1 (en) * | 2004-05-28 | 2005-12-15 | International Innovations Limited | Clutch |
US20080176686A1 (en) * | 2007-01-19 | 2008-07-24 | Denso Corporation | Torque transmission device with enhanced ability to absorb change in rotation between torque input and output member |
US20100288595A1 (en) * | 2009-05-18 | 2010-11-18 | Korea Advanced Institute Of Science And Technology | Disk friction clutch apparatus using self-energizing effect |
CN102734343A (en) * | 2011-04-07 | 2012-10-17 | Zf腓德烈斯哈芬股份公司 | Device for changing operational status of shifting element with two shifting element halves |
WO2020088873A1 (en) * | 2018-10-31 | 2020-05-07 | Bayerische Motoren Werke Aktiengesellschaft | Clutch assembly for a motor vehicle drivetrain, and motor vehicle drivetrain |
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SE519490C2 (en) * | 2001-07-05 | 2003-03-04 | Haldex Traction Ab | Ball arrangement in a torque transmitting device |
US6808037B1 (en) * | 2003-04-08 | 2004-10-26 | New Venture Gear, Inc. | On-demand transfer case |
US7021442B2 (en) * | 2004-03-16 | 2006-04-04 | General Motors Corporation | One-way torque transmitter with a friction actuating apparatus |
US20050279601A1 (en) * | 2004-06-17 | 2005-12-22 | Thomas Tuday | Torque-transmitting mechanisms for a planetary transmission |
US7357748B2 (en) * | 2004-07-13 | 2008-04-15 | Borgwarner Inc. | Limited slip differential |
US8231492B2 (en) | 2009-04-16 | 2012-07-31 | GM Global Technology Operations LLC | Torque transmitting device |
US9701195B2 (en) | 2013-06-14 | 2017-07-11 | Dana Automotive Systems Group, Llc | Differential with torque coupling |
US9625024B2 (en) * | 2013-06-14 | 2017-04-18 | Dana Automotive Systems Group, Llc | Differential with torque coupling |
JP6451964B2 (en) | 2014-07-16 | 2019-01-16 | デーナ、オータモウティヴ、システィムズ、グループ、エルエルシー | Drive unit with twin side shaft torque coupling and method for coupling torque through the twin side shaft of the drive unit |
US10626929B2 (en) * | 2016-05-09 | 2020-04-21 | Team Industries, Inc. | Dual clutch |
US10197144B2 (en) | 2017-01-20 | 2019-02-05 | Dana Heavy Vehicle Systems Group, Llc | Drive unit with torque vectoring and an axle disconnect and reconnect mechanism |
CN215171993U (en) * | 2020-03-02 | 2021-12-14 | 伊顿智能动力有限公司 | Differential and electromagnetic differential |
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US20030094343A1 (en) * | 2001-11-21 | 2003-05-22 | Showalter Dan Joseph | Ball ramp clutch having force amplifying configuration |
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US6578693B2 (en) * | 2000-04-07 | 2003-06-17 | Gkn Viscodrive Gmbh | Axial setting device |
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GB2235957B (en) * | 1989-08-31 | 1993-06-30 | Gkn Automotive Ag | Gearbox |
JP3104565B2 (en) * | 1995-03-24 | 2000-10-30 | トヨタ自動車株式会社 | Clutch device |
-
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- 2002-11-25 US US10/303,530 patent/US6742642B1/en not_active Expired - Fee Related
-
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- 2003-11-25 DE DE10355071A patent/DE10355071B4/en not_active Expired - Fee Related
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US2827994A (en) * | 1954-10-18 | 1958-03-25 | Curtiss Wright Corp | Follow-up clutches |
USRE36502E (en) * | 1994-01-31 | 2000-01-18 | Eaton Corporation | Clutch ball ramp actuator with drive and coast apply |
US5659235A (en) * | 1995-02-22 | 1997-08-19 | Hitachi, Ltd. | Drive controller and control method for electric vehicle |
US6578693B2 (en) * | 2000-04-07 | 2003-06-17 | Gkn Viscodrive Gmbh | Axial setting device |
US6460677B1 (en) * | 2000-11-28 | 2002-10-08 | Spicer Technology, Inc. | Dual ball ramp actuator for locking differential |
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Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2005119076A1 (en) * | 2004-05-28 | 2005-12-15 | International Innovations Limited | Clutch |
US20080047797A1 (en) * | 2004-05-28 | 2008-02-28 | Steve Hargreaves | Clutch |
US20080176686A1 (en) * | 2007-01-19 | 2008-07-24 | Denso Corporation | Torque transmission device with enhanced ability to absorb change in rotation between torque input and output member |
US20100288595A1 (en) * | 2009-05-18 | 2010-11-18 | Korea Advanced Institute Of Science And Technology | Disk friction clutch apparatus using self-energizing effect |
US8348038B2 (en) * | 2009-05-18 | 2013-01-08 | Korea Advanced Institute Of Science And Technology | Disk friction clutch apparatus using self-energizing effect |
CN102734343A (en) * | 2011-04-07 | 2012-10-17 | Zf腓德烈斯哈芬股份公司 | Device for changing operational status of shifting element with two shifting element halves |
WO2020088873A1 (en) * | 2018-10-31 | 2020-05-07 | Bayerische Motoren Werke Aktiengesellschaft | Clutch assembly for a motor vehicle drivetrain, and motor vehicle drivetrain |
CN112601898A (en) * | 2018-10-31 | 2021-04-02 | 宝马股份公司 | Clutch assembly for a motor vehicle drive train and motor vehicle drive train |
US11346419B2 (en) | 2018-10-31 | 2022-05-31 | Bayerische Motoren Werke Aktiengesellschaft | Clutch assembly for a motor vehicle drivetrain, and motor vehicle drivetrain |
Also Published As
Publication number | Publication date |
---|---|
DE10355071A1 (en) | 2004-06-09 |
DE10355071B4 (en) | 2005-08-04 |
US6742642B1 (en) | 2004-06-01 |
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Legal Events
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AS | Assignment |
Owner name: GENERAL MOTORS CORPORATION, MICHIGAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:STEVENSON, PAUL D.;CAREY, CLINTON E.;REEL/FRAME:013766/0514 Effective date: 20021108 |
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Year of fee payment: 4 |
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