WO2014110144A1 - Différentiel à glissement limité qui utilise des engrenages à denture frontale et un carter de pignon - Google Patents

Différentiel à glissement limité qui utilise des engrenages à denture frontale et un carter de pignon Download PDF

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Publication number
WO2014110144A1
WO2014110144A1 PCT/US2014/010699 US2014010699W WO2014110144A1 WO 2014110144 A1 WO2014110144 A1 WO 2014110144A1 US 2014010699 W US2014010699 W US 2014010699W WO 2014110144 A1 WO2014110144 A1 WO 2014110144A1
Authority
WO
WIPO (PCT)
Prior art keywords
differential
face
pinion housing
pinion
housing
Prior art date
Application number
PCT/US2014/010699
Other languages
English (en)
Inventor
Paul N. Herrmann
Steven J. Cochren
Sandeep Kumar
Steven A. Rudko
Stephen P. Radzevich
Matthew G. Fox
Daniel Philip FISHER
Original Assignee
Eaton Corporation
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from US13/737,713 external-priority patent/US9664271B2/en
Application filed by Eaton Corporation filed Critical Eaton Corporation
Priority to DE212014000031.9U priority Critical patent/DE212014000031U1/de
Priority to CN201490000381.7U priority patent/CN205173406U/zh
Publication of WO2014110144A1 publication Critical patent/WO2014110144A1/fr

Links

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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • 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
    • 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
    • F16H2048/102—Differential gearings with gears having orbital motion with orbital spur gears with spur gears engaging face 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
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H2048/204—Control of arrangements for suppressing differential actions
    • F16H2048/207—Control of arrangements for suppressing differential actions using torque sensors

Definitions

  • the present invention relates to a housing configured to support pinions in a differential, and embodiments include a differential incorporating a torque ring or pinion housing configured to support pinions.
  • a differential comprises a differential case; a side gear comprising a helical face gear; a helical pinion configured for operative or meshing engagement with the side gear; and a pinion housing.
  • the pinion housing is configured to support the helical pinion and includes: a first face; a second face opposing the first face; a first projection located on the first face; and a second projection located on the second face.
  • the differential further comprises an actuator configured for engagement with the pinion housing.
  • the actuator comprises a first face that includes a depression substantially corresponding in shape to the first projection or the second projection on the pinion housing.
  • the differential further comprises a plurality of friction plates disposed between the actuator and the differential case. With other embodiments, friction plates or thrust washers may be reduced or entirely eliminated.
  • a housing is configured to support at least one helical pinion in a differential and comprises a generally annular ring.
  • the generally annular ring has a first face and a first projection located on the first face and extending in the axial direction of the generally annular ring.
  • the generally annular ring also has a second face and a second projection located on the second face and extending in the axial direction of the generally annular ring.
  • the generally annular ring also has an aperture or hole extending radially inwardly from an outer radial surface of the generally annular ring.
  • the generally annular ring also has a channel extending from the first face to the second face, wherein the channel is substantially radially aligned with the aperture or the hole.
  • the pinion housing or torque ring may not be bolted or otherwise rigidly secured to a differential or transfer case. Rather, the pinion housing or torque ring may be permitted to move or "float" in an axial direction, along with associated pinions, between two side gears. Such pinion housing or torque ring may be coupled to or configured for engagement with a differential or transfer case.
  • FIG. 1 is an exploded perspective view of a differential in accordance with an embodiment of the disclosure.
  • FIG. 2 is a cross-sectional view of a differential in accordance with an embodiment of the disclosure.
  • FIG. 3 is a perspective view of a pinion housing of the differential of FIG. 1.
  • FIG. 4 is a perspective view of a pinion and a side gear of the differential of FIG.
  • FIG. 5 is a perspective view of an actuator of the differential of FIG. 1.
  • FIG. 6 is a perspective view of the actuator of FIG. 5 disposed in a differential case of the differential of FIG. 1.
  • FIGS. 7A-7B are schematic views of force acting on the pinion housing of FIG.
  • FIG. 8 is a cross-sectional view of a portion of a differential in accordance with an embodiment of the disclosure.
  • FIGS. 9A and 9B are exploded perspective views of differentials in accordance with embodiments of the disclosure.
  • FIGS. 10A and 10B are cross-sectional views of differentials in accordance with embodiments of the disclosure.
  • FIGS. 11 A and 1 IB are perspective views of pinion housings in accordance with embodiments of the disclosure.
  • FIG. 12 is a perspective view of a pinion housing in accordance with another embodiment of the disclosure.
  • FIGS. 1-2 generally illustrate an embodiment of differential 10 shown in accordance with teachings of the present invention.
  • Differential 10 may comprise a pinion housing 12 (which may also be referred to in some contexts or environments as a "torque ring").
  • pinion housing 12 may be made from one piece of material (e.g., comprise a unitary, integral, and/or monolithic structure) in accordance with an
  • Pinion housing 12 may be generally ring-shaped in accordance with an embodiment of the invention.
  • Pinion housing 12 may comprise an outer radial surface 14 that extends circumferentially around the pinion housing 12.
  • Pinion housing 12 may further comprise a first face 16 and a second face 18. The second face 18 may oppose the first face 16.
  • the pinion housing 12 may include a first projection 20 located on the first face
  • the first projection 20 may extend in the axial direction of the generally annular ring comprising the pinion housing 12.
  • the pinion housing 12 may further include a second projection 22 located on the second face 18.
  • the second projection 22 may extend in the axial direction of the generally annular ring comprising the pinion housing 12.
  • the pinion housing 12 may include a single projection 20 on the first face 16, and a single projection 22 on the second face 18 in an embodiment of the invention.
  • the pinion housing 12 may include a plurality of projections 20 on the first face 16 and/or a plurality of projections 22 on the second face 18 in accordance with some embodiments of the invention. At least one of the first projections 20 may comprise a ramp or a wedge in accordance with an embodiment of the invention.
  • Each of the first projections 20 may comprise a ramp or a wedge in accordance with an embodiment of the invention.
  • At least one of the second projections 22 may comprise a ramp or a wedge in accordance with an embodiment of the invention.
  • Each of the second projections 22 may comprise a ramp or a wedge in accordance with an embodiment of the invention.
  • At least one of the first projections 20 may comprise a plurality of surfaces in accordance with an embodiment of the invention.
  • at least one of the surfaces may be substantially parallel to the first face 16, and at least one of the surfaces may be substantially angled relative to the first face 16.
  • At least one of the second projections 22 may comprise a plurality of surfaces in accordance with an embodiment of the invention.
  • at least one of the surfaces may be substantially parallel to the second face 18, and at least one of the surfaces may be substantially angled relative to the second face 18.
  • at least one of the first projections 20 and/or second projections 22 may comprise about three surfaces.
  • first and second projections 20, 22 may comprise fewer or more surfaces in accordance with various embodiments of the invention.
  • Pinion housing 12 may be configured for locating and/or supporting one or more pinions 24.
  • the pinions 24 may be disposed in a radial pattern or the pinions 24 may be circumferentially spaced around the circumference of the pinion housing 12.
  • the pinion housing 12 may have a plurality of radially inwardly extending apertures or holes 26.
  • the apertures 26 may extend radially inwardly into the pinion housing 12 from the outer radial surface 14 of the pinion housing 12.
  • the apertures 26 may each have an axis that extends substantially radially outwardly from the approximate center of the pinion housing 12. At least one of the first projections 20 of the pinion housing 12 may be located proximate aperture 26.
  • At least one of the second projections 22 of the pinion housing 12 may be located proximate aperture 26.
  • six apertures 26 are mentioned in detail, there may be fewer or more apertures 26 in other embodiments of the invention.
  • the apertures 26 may be equi-angularly spaced around the circumference of the pinion housing 12.
  • the apertures 26 are described as being equi-angularly spaced around the circumference of the pinion housing 12, the apertures 26 may be spaced in any alternate arrangements and/or configurations in other embodiments of the invention.
  • the pinion housing 12 may further comprise an inner radial surface 28.
  • the pinion housing 12, including the inner radial surface 28 may be configured to restrain the pinions 24 from axial movement.
  • the inner radial surface 28 may extend circumferentially around the pinion housing 12, such that each of apertures 26 may comprise a blind aperture.
  • a first end of the aperture 26 at the outer radial surface 14 may be open, while a second end of the aperture 26 at the inner radial surface 28 may be closed.
  • the second end of the aperture 26 may oppose the first end of the aperture 26.
  • the pinion housing 12 may further include a channel 30 extending from the first face 16 to the second face 18 of the generally annular ring of the pinion housing 12.
  • the channel 30 may be substantially aligned with the apertures 26 (e.g.,
  • the pinion housing 12 may be configured to support the pinions 24 to be in operative or meshing engagement with side gears 32.
  • the pinion housing 12 has been removed in FIG. 4 for illustrative purposes, and FIG. 4 generally illustrates the operative or meshing engagement between pinions 24 and side gears 32.
  • the pinion housing 24 may exert pressure on the pinions 24 to move them around and/or about an axial center line of the side gears 32.
  • the differential 10 may comprise the pinions 24.
  • Pinion 24 may comprise a helical pinion.
  • pinion 24 may include a number of helical teeth. The number of helical teeth and the geometry of the tooth flank of the helical teeth may vary in accordance with various embodiments of the invention.
  • the helical pinion 24 may be generally cylindrical in accordance with an embodiment of the invention, although the shape of the helical pinion may vary in accordance with various embodiments of the invention.
  • the number of the pinions 24 in the differential 10 may vary. However, there may generally be at least two pinions 24.
  • the number of pinions 24 may be about six in an embodiment, although greater or fewer pinions 24 may be used in other embodiments.
  • the number of pinions 24 may generally correspond to the number of apertures 26 in the pinion housing 12, although fewer pinions 24 in relation to the number of apertures 26 may be used in embodiments of the invention. In these embodiments of the invention, at least one or more of the apertures 26 may remain open.
  • the size of pinions 24 may also vary, but may generally be sized so as to fit operatively within the apertures 26 of the torque ring so as to allow the pinions 24 to be free to rotate within apertures 26.
  • the pinions 24 may generally be axially trapped between the inner radial surface 28 of the pinion housing 12 and an inner surface of a differential case (or other housing for the pinion housing 12).
  • the differential 10 may further comprise the side gears 32.
  • Side gears 32 may have a helical face (i.e., comprise helical face gears). Accordingly, side gears 32 may include a number of helical teeth. The number of helical teeth and the geometry of the tooth flank of the helical teeth may vary in accordance with various
  • helical face gears comprising the side gears 32 may be robust and well-supported.
  • the use of high strength helical face gears may allow for higher torque application and provide a wider range of torque bias ratio.
  • the compact size of side gears 32 comprising helical face gears in connection with a pinion housing 12 may allow for greater flexibility in packaging and design, thereby increasing the transportability of a differential that includes the side gears 32.
  • helical face technology may allow for the use of the side gears 32 in connection with various packaging designs of various models of motor vehicles.
  • the compact size of side gears 32 comprising helical face gears in connection with a pinion housing 12 may also allow for the direction of dynamic forces in a more beneficial way.
  • each side gear 32 may face pinion housing 12.
  • the side gears 32 may be configured to be in operative or meshing engagement with the pinions 24.
  • the helical teeth of the side gears 32 may be in an operative, or meshing, engagement with the helical teeth of the pinions 24.
  • Both the helical teeth of the side gears 32 and the helical teeth of the pinions 24 may extend into channels 30 in the pinion housing 12.
  • the side gears 32 With a configured meshing engagement between the pinions 24 and the side gears 32, the side gears 32 may be forced to turn about their axis.
  • the side gears 32 may be configured to transmit torque from the pinions 24 to an output (e.g., axle shafts of a motor vehicle).
  • a motor vehicle incorporating the differential 10 may move.
  • the pinions 24 may rotate within the pinion housing 12 and in mesh with the side gears 32 to compensate.
  • a first and second side gear 32 may be disposed on opposing sides of the pinion housing 12.
  • Each side gear 32 may have a first annular hub portion 34 that is configured to receive an axle shaft (not shown) of a motor vehicle, for example.
  • An inner radial surface of the first annular hub portion 34 of the side gear 32 that may include a plurality of splines.
  • the axle shafts may connect to side gears 32 through a splined interconnection with the splines.
  • the differential 10 may further comprise an actuator 36.
  • Actuator 36 may be configured for engagement with the pinion housing 12.
  • Actuator 36 may be generally ring-shaped in accordance with an embodiment of the invention.
  • Actuator 36 may comprise an outer radial surface 38 that extends circumferentially around the actuator 36.
  • Actuator 36 may further comprise a first face 40 and a second face 42.
  • the second face 42 may oppose the first face 40.
  • the actuator 36 may include a depression 44 located on the first face 40.
  • the actuator 36 may include a single depression 44 on the first face 40 in an embodiment of the invention.
  • the actuator 36 may include a plurality of depressions 44 on the first face 40 in accordance with some embodiments of the invention.
  • the depression 44 may generally correspond in shape to the first projection 20 or the second projection 22 on the pinion housing 12.
  • the first face 40 may be configured to face the pinion housing 12 in an embodiment of the invention.
  • At least one of the depressions 44 may comprise a plurality of surfaces in accordance with an embodiment of the invention.
  • at least one of the surfaces may be substantially parallel to the first face 40, and at least one of the surfaces may be substantially angled relative to the first face 40.
  • at least one of the depressions 44 may comprise about three surfaces.
  • a depression comprising three surfaces is mentioned in detail and generally illustrated, the depression 44 may comprise fewer or more surfaces in accordance with various embodiments of the invention.
  • the second face 42 of the actuator 36 may be generally or substantially flat in accordance with an embodiment of the invention.
  • the second face 42 of the actuator 36 may not have a depression.
  • the outer radial surface 38 of the actuator 36 may comprise at least one and/or a plurality of radially extending tabs 46.
  • the actuator 36 may include three tabs 46.
  • the actuator may have fewer or more tabs 46 in accordance with other embodiments of the invention.
  • the tabs 46 may be equi-angularly spaced around the circumference and/or periphery of the actuator 36.
  • the tabs 46 may be approximately 120° apart in accordance with an embodiment of the invention.
  • Tabs 46 may be generally configured for engagement with the differential case 50.
  • tabs 46 may be configured for engagement with slots in the differential case 50.
  • FIG. 6 generally shows the actuator 36 disposed in differential case 50.
  • torque may be transferred from the differential case 50 to the actuator 36.
  • the actuator 36 may be configured to drive the pinion housing 12.
  • the actuator 36 may be configured to lock the pinions 24 with both side gears 32, pushing both friction plate assemblies 48 and transferring torque to both wheels of a motor vehicle (not shown) simultaneously.
  • the differential 10 may further comprise friction plate assemblies 48 (e.g., a plurality of friction plates).
  • the friction plate assemblies 48 may be disposed on both sides of the pinion housing 12.
  • the friction plate assemblies 48 may be disposed between the actuator 36 and the differential case 50.
  • At least one of the plurality of friction plates of the friction plate assembly 48 may include a coating.
  • at least one of the plurality of friction plates of the friction plate assembly 48 may include a coating configured to aid the friction plates to react to movement between the side gears 32 and the differential case 50.
  • the axial force exerted by the actuator 36 may generally depend on the input torque and the ramp or wedge angle on the actuator 36.
  • both of the wheels may have different resistive torque and rotational speed.
  • differential action may make the friction plate assemblies 48 slip and allow the outer wheel to rotate faster than the inner wheel, for example. If one wheel slips as a result of a low friction surface beneath the wheel, the pinion housing 12 may be configured to generate an axial force against the actuator 36.
  • FIGS. 7A-7B a schematic of the reaction force is generally illustrated. This may result in compression of the friction plate assemblies 48 against the side gears 32, thereby transferring torque from the differential case 50 to the side gear 32 through the friction plate assembly 48.
  • FIG. 7A-7B a schematic of the reaction force is generally illustrated. This may result in compression of the friction plate assemblies 48 against the side gears 32, thereby transferring torque from the differential case 50 to the side gear 32 through the friction plate assembly 48.
  • Differential case 50 may be provided to house the pinion housing 12, the pinions 24, the side gears 32 and/or any number of other components of the differential 10.
  • the differential 10 may further include a ring gear (not shown).
  • the ring gear may be connected to an input source and/or drive source (not shown) in a conventional manner for rotating the differential case 50.
  • the differential 10 may further include thrust washers 54. Thrust washers 54 may be provided between a thrust face of the differential case 50 and a thrust face of the side gear 32 and between a thrust face of the cover 52 and a thrust face of the side gear 32. Thrust washers 54 may be provided to control backlash, as the friction pack assemblies 48 may become isolated from the axial thrust force of the side gears 32.
  • the pinion housing (or torque ring) 12 may not be bolted or otherwise rigidly secured to a transfer case. Instead, the pinion housing 12 may be permitted to move or "float" in an axial direction, along with associated pinions 24, between two side gears 32. Such pinion housing 12 may be coupled to or configured for engagement with a differential or transfer case.
  • Permitting the pinion housing (or torque ring) 12 to move (or float) axially as disclosed can, inter alia, maintain the ability to transfer torque from the associated case to the gear set, and may improve gear teeth coupling or mesh (compared with a pinion housing that is bolted or rigidly fixed to a case). Such flexibility in positioning can also permit the pressure to self-equalize on each side of the pinion housing 12. Improving gear teeth mesh can, among other things, improve gear performance, gear durability, and gear life.
  • the pinion housing 12 houses associated pinions (or pinion gears) 24 and is configured to transfer torque from the case to the side gears 32 via the pinions 24.
  • the pinion housing (or torque ring) 12 is configured to move (or float) axially, along with the housed pinions 24, between the side gears 32. Such a configuration can permit the pinions 24 to have better freedom of movement for fit (e.g., to optimize their positions) with respect to the side gears 32. Improved meshing between the pinions 24 and the side gears 32 can, among other things, provide improved gear life. While the pinion housing 12 is configured to move axially, as noted, the pinion housing can be coupled to the differential (or transfer case) in a number of ways, including the exemplar ways disclosed herein, to transfer torque.
  • FIGS. 9 and 10 generally illustrate exploded perspective views of differentials configured in accordance with teachings of the disclosure.
  • the differential 10 may include thrust washers 54 (see, e.g., FIG. 9A) and friction plates, embodiments permitting the pinion housing 12 to move axially may reduce, or even entirely eliminate, thrust washers and/or friction plates.
  • pinions 24 may be shown with pinion guides 25 (e.g., as illustrated in FIG. 9B), with embodiments such guides may be unnecessary or may be intentionally eliminated.
  • pinion guides 25 and related apertures can, among other things improve assembly and reduce associated manufacturing costs.
  • the side gears 32 may be forged and the pinions 24 may be hobbed.
  • the pinion housing may include one or more transfer formations 60.
  • Such transfer formation(s) 60 may be configured to engage or be coupled with a differential or transfer case to transfer torque.
  • a plurality of transfer formations 60 are shown extending radially outwardly from an outer radial surface 62 of the pinion housing 12.
  • Such transfer formations 60 may take various numbers, spacing, shapes, forms, and sizes including, without limitation, those characterized as outer diameter lugs or splines.
  • FIGS. 10A and 10B generally illustrate cross-sectional views of differentials configured in accordance with embodiments of the disclosure.
  • FIGS. 11A and 1 IB generally illustrate another embodiment of a pinion housing
  • transfer formations 60 may take various numbers, spacing, shapes, forms, and sizes, including, without limitation, axial lugs such as generally illustrated.
  • one or more transfer formations may be provided on and extend from both an axial and a radial surface of the pinion housing (e.g., including transfer formations such as shown in FIG. 11 A and FIG. 12).

Abstract

La présente invention se rapporte à un différentiel qui comprend un carter de différentiel ; un engrenage latéral ; un pignon configuré pour s'engrener avec l'engrenage latéral ; et un carter de pignon configuré pour supporter le pignon. Le carter de pignon comprend une première face ; une seconde face opposée à la première face ; une première saillie située sur la première face ; et une seconde saillie située sur la seconde face. Le carter de pignon comprend également une ouverture ou un trou qui s'étend radialement vers l'intérieur depuis une surface radiale externe de la bague généralement annulaire ; et un canal qui s'étend depuis la première face jusqu'à la seconde face, le canal étant sensiblement radialement aligné avec l'ouverture ou le trou. Dans certains modes de réalisation, le carter de pignon comprend un ou plusieurs dispositifs de transfert configurés pour transférer le couple depuis le carter différentiel et le carter de pignon est configuré pour permettre un déplacement dans une direction axiale entre une paire d'engrenages latéraux.
PCT/US2014/010699 2013-01-09 2014-01-08 Différentiel à glissement limité qui utilise des engrenages à denture frontale et un carter de pignon WO2014110144A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE212014000031.9U DE212014000031U1 (de) 2013-01-09 2014-01-08 Differential mit begrenztem Schlupf, Kronenrädern und einem Ritzelgehäuse
CN201490000381.7U CN205173406U (zh) 2013-01-09 2014-01-08 使用端面齿轮和小齿轮壳体的限滑差速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US13/737,713 2013-01-09
US13/737,713 US9664271B2 (en) 2009-06-12 2013-01-09 Limited slip differential using face gears and a pinion housing

Publications (1)

Publication Number Publication Date
WO2014110144A1 true WO2014110144A1 (fr) 2014-07-17

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PCT/US2014/010699 WO2014110144A1 (fr) 2013-01-09 2014-01-08 Différentiel à glissement limité qui utilise des engrenages à denture frontale et un carter de pignon

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Country Link
CN (1) CN205173406U (fr)
DE (1) DE212014000031U1 (fr)
WO (1) WO2014110144A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017004933A1 (de) * 2017-05-20 2018-11-22 Daimler Ag Differentialgetriebe für ein Kraftfahrzeug
US20180347637A1 (en) * 2017-05-31 2018-12-06 GM Global Technology Operations LLC Pinion Flange With Dampening Member

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Publication number Priority date Publication date Assignee Title
JPH08135770A (ja) * 1994-11-09 1996-05-31 Tochigi Fuji Ind Co Ltd デファレンシャル装置
US20090105032A1 (en) * 2007-10-18 2009-04-23 Gkn Driveline Torque Technology Kk Differential gear
US20100317482A1 (en) * 2009-06-12 2010-12-16 Eaton Corporation Limited slip differential using face gears and a pinion housing
US8133146B2 (en) * 2009-04-14 2012-03-13 Eaton Corporation Gear train with split torque
US20120077635A1 (en) * 2007-08-14 2012-03-29 Autotech Sport Tuning Corporation Differential gear assembly

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3253483A (en) 1963-03-06 1966-05-31 Thomas M Mccaw Differential
US4791832A (en) 1985-12-05 1988-12-20 Mccaw Thomas M Caged helical gear differential

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08135770A (ja) * 1994-11-09 1996-05-31 Tochigi Fuji Ind Co Ltd デファレンシャル装置
US20120077635A1 (en) * 2007-08-14 2012-03-29 Autotech Sport Tuning Corporation Differential gear assembly
US20090105032A1 (en) * 2007-10-18 2009-04-23 Gkn Driveline Torque Technology Kk Differential gear
US8133146B2 (en) * 2009-04-14 2012-03-13 Eaton Corporation Gear train with split torque
US20100317482A1 (en) * 2009-06-12 2010-12-16 Eaton Corporation Limited slip differential using face gears and a pinion housing

Also Published As

Publication number Publication date
CN205173406U (zh) 2016-04-20
DE212014000031U1 (de) 2015-09-02

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