EP2024197A1 - Unité de transmission destinée à transmettre un couple d'entraînement d'un arbre d'entrée à deux arbres de sortie - Google Patents

Unité de transmission destinée à transmettre un couple d'entraînement d'un arbre d'entrée à deux arbres de sortie

Info

Publication number
EP2024197A1
EP2024197A1 EP07729511A EP07729511A EP2024197A1 EP 2024197 A1 EP2024197 A1 EP 2024197A1 EP 07729511 A EP07729511 A EP 07729511A EP 07729511 A EP07729511 A EP 07729511A EP 2024197 A1 EP2024197 A1 EP 2024197A1
Authority
EP
European Patent Office
Prior art keywords
transmission
switching element
braking device
differential
output shafts
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.)
Ceased
Application number
EP07729511A
Other languages
German (de)
English (en)
Inventor
Alois BÖCK
Detlef Baasch
Robert Peter
Florian Knedler
Michael Donaubauer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2024197A1 publication Critical patent/EP2024197A1/fr
Ceased legal-status Critical Current

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
    • F16H48/30—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
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel 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
    • 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
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/295—Arrangements for suppressing or influencing the differential action, e.g. locking devices using multiple means for force boosting
    • 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
    • F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
    • F16H2048/343—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a rotary 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
    • F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
    • F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement

Definitions

  • Transmission unit for guiding a drive torque from a drive shaft to two output shafts
  • the invention relates to a Getriebeeinheif for guiding a drive torque from a drive shaft to two output shafts according to the closer defined in the preamble of claim 1.
  • Such a gear unit is known for example from FR 2 864 190. It describes an asymmetrical transfer case which distributes a drive torque generated by a drive motor by means of a differential unit to two wheels connected to an output shaft. A differential of the differential unit divides the drive torque evenly on the two output shafts.
  • each of the two output shafts is associated with a so-called torque vectoring unit with a planetary set, which is arranged between a differential cage of the differential unit and the respective output shaft and with which to the respective Output shaft acting drive torque can be influenced.
  • the web of the planetary gear set to generate a so-called Torque-Vectoring- be braked by means of a brake relative to a transmission housing, whereby the supported on the gearbox torque vectoring torque by means realized with the planetary gears and the sun gears of the planetary gear set stage on the respective wheel is guided.
  • the respective output shaft and the differential cage are in each case fixedly connected to a sun gear of the planetary gear set, wherein the sun gears each have a planet gear arranged on the planet. mencade.
  • a planetary carrier of the planetary gearset is rotatably connected to the planets, wherein a bearing of the planet carrier is located in a region of the planetary gearset facing away from a transmission center.
  • the brake which is arranged on the planet carrier of the planetary gear set, is arranged with respect to a longitudinal axis of the output shafts radially outside of an axis of the planets.
  • the present invention has for its object to design a transmission unit of the type mentioned above such that a braking device for operating a device for influencing the degree of distribution of the drive torque to the driven wheels while ensuring the secure functionality with a small size is inexpensive to deploy,
  • a transmission unit in particular a Schuachsgetriebeiki, provided for guiding a drive torque from a drive shaft to two output shafts via a differential unit and a switchable by means of at least one motor, continuously adjustable device for influencing the degree of distribution of the drive torque to the output shafts, wherein the differential unit is a differential and a differential cage operatively connected to the drive shaft, and the device for influencing the degree of distribution of the drive torque sung tion of the degree of distribution of the drive torque has at least one planetary gear set as a translation stage, which is operatively connected to the differential cage and an associated output shaft and which has a braking device.
  • the differential unit is a differential and a differential cage operatively connected to the drive shaft
  • the device for influencing the degree of distribution of the drive torque sung tion of the degree of distribution of the drive torque has at least one planetary gear set as a translation stage, which is operatively connected to the differential cage and an associated output shaft and which has a braking device.
  • the braking device is laterally offset in the direction of a planetary axis next to Planenten the translation stage and at least approximately within a radial Warre- ckungs Schemees of the planet around a longitudinal axis of the output shafts.
  • the braking device and in particular its actuator due to the positioning laterally next to the planets and radially in the vicinity of the longitudinal axis of the output shafts advantageously be made very small, thereby saving space and also the manufacturing costs are reduced.
  • the entire transmission unit can be made smaller or space for other components can be created.
  • the braking device is arranged with respect to a transmission center axis which is perpendicular to the longitudinal axis of the output shafts either in a region facing a transmission center or in a region remote from the transmission center next to the planet.
  • the braking device with a switching element such.
  • the switching element can both on one of the transmission center facing away on one side of the gearset and the planetary gear set in the direction of the planetary axis between be arranged the means for axial adjustment and the planetary gear set.
  • the device for axial adjustment can also be arranged on one of the transmission center facing away as well as on a side facing away from the transmission center side planetary gear set in the direction of the planetary axis between the switching element and the planetary gearset.
  • the switching element of the braking device is designed as a multi-disc brake.
  • the smaller dimensionability of the braking device in smaller diameters of the slats affects.
  • the positioning of the brake device according to the invention occur in the multi-disc brake when not in operation only small drag losses, since the fins rotate at about the wheel speed, and the friction speeds are relatively low at high speeds.
  • the multi-disc brake can be actuated by means of an operable by at least one motor for axial adjustment such that the drive shaft of the motor interacts with a pivot wheel of the device for axial adjustment, wherein the swivel wheel formed by particular trained as balls rolling elements in depth varying grooves of the swivel wheel and in correspondingly arranged grooves of a housing fixed ball ramp disc of the device for axial adjustment, cooperating with the ball ramp disc.
  • the positioning of the brake device according to the invention has the advantageous effect that there is greater freedom in the choice of manufacturing technology of the actuator and the manufacturing costs can be reduced accordingly.
  • the pressure axis of the ball ramp disk can advantageously be in the range of the diameter of the slats.
  • Figure 1 is a partially schematic sectional view of a Häachsgetriebeiki of a motor vehicle with a planetary gear set designed as a translation stage, which is formed with a with a switching element and a switching element actuated means for axial adjustment formed braking device.
  • FIG. 2 shows a partially sectional view of the Schusachssgetriebeischen of FIG. 1 with an alternative arrangement of the braking device.
  • a portion of a transmission unit 1 is shown which one of a only schematically illustrated engine or internal combustion engine 10, transmitted via a drive shaft 2 drive torque to a first output shaft 3 and a coaxial thereto and with respect to the drive shaft 2 symmetrically arranged second Abfriebswelle 5 distributed.
  • the gear unit 1 is provided for installation in a motor vehicle and is designed in the embodiment shown as Schuachsgetriebetician, but it is also conceivable that a substantially analog gear unit is used as Vorderachsgetriebetician. It is also conceivable to use the present transmission unit both as a front axle transmission unit and as a rear axle transmission unit, for example in a four-wheel drive motor vehicle.
  • the output shafts 3 and 5 which are rotatably mounted about a common longitudinal axis X, are connected at their free ends in each case with a vehicle wheel, not shown, wherein in the installed state of the Schuachsgetriebeiki 1 a vehicle with respect to the output shaft 3 on a viewed in the vehicle front left Transmission side 7 and a vehicle wheel with respect to the output shaft 5 on a right side gear 9 is located.
  • the Hinterachsgetriebetician 1 includes a transmission housing 11, which with a substantially surrounding the drive shaft 2 front gear housing part 12, with one of the left side gear 7 associated side gear housing part 13 from which protrudes the first output shaft 3 side, and with a not shown the right side of the transmission 9 associated lateral gear housing part, from which the second output shaft 5 protrudes laterally, is formed.
  • the rear axle transmission unit 1 distributes the drive torque transmitted from the drive shaft 2 to the two output shafts 3 and 5 and can thereby also effect an uneven torque distribution on the two output shafts 3 and 5 and thus actively improve the driving characteristics.
  • the drive torque is introduced from the drive shaft 2 in a differential unit 15, which with a differential 17 and a differential cage 19th is formed and connected to a device 14 for influencing the drive torque to the output shafts 3 and 5.
  • differential cage 19 For operative connection between the drive shaft 2 and the differential cage 19 is fixedly connected to the drive shaft 2 drive pinion 21 with a fixed connected to the differential cage 19 ring gear 23 into engagement, wherein the differential cage 19 is rotatably mounted about the longitudinal axis X and in the transmission housing 11th supported.
  • the differential 17 is formed in a manner known per se with two output-side bevel gears 25 and 27 connected to the respective output shaft 3 and 5 and with two bevel gears 29 and 31 meshing with the two bevel gears 25 and 27.
  • the two bevel gears 29 and 31 are rotatably mounted on a bolt 33 which is fixed in the differential cage 19 with respect to a rotation about the longitudinal axis X.
  • Fig. 1 shows two embodiments of the drive side bevel gears 29 and 31 and the cooperating output side bevel gears 27 and 25, which are each engaged with each other, the expert can select an alternative according to the particular application.
  • the bevel gears 29 and 31 rotate with the bolt 33 exclusively about the longitudinal axis X. Should an output shaft in the installed state, for example, rotate faster than when cornering at different speeds rotating vehicle wheels the other, then rotate the drive side bevel gears 29 and 31 to compensate for the speed difference around the bolt 33, wherein the bolt 33 further passes the drive torque via its rotation about the longitudinal axis X on the two output shafts 3, 5.
  • the device 14 is provided for influencing the drive torque to the output shafts 3 and 5 with two symmetrical to the transmission axis Y arranged identical Torque vectoring units, of the two torque vectoring units in Fig. 1, only the left transmission side 7 associated with torque-representing unit 35, which will be described below.
  • the torque vectoring units are arranged in the gear housing 11 and are in the present case continuously adjusted and actuated by an associated, switchable electric motor 37.
  • the illustrated torque vectoring unit 35 has a planetary gear set formed as an upper stage 39 and an actuatable by the electric motor 37 brake device 51, wherein the Translation stage 39 is formed with two sun gears 61 and 63, of which a first sun gear 61 fixed to the differential cage 19 and of which a second sun gear 63 is fixedly connected to the output shaft 3.
  • the sun gears 61 and 63 cooperate with present three rotatably mounted on a planetary carrier 65 planet, of which two planets 69 and 71 are visible, and which have a continuous toothing 73.
  • the braking device 51 is formed with a designed as a multi-disc brake 77 switching element and a cooperating with the switching element means 87 for axial adjustment.
  • the with respect to their transmission capability infinitely adjustable multi-disc brake 77 has arranged on the planet carrier 65 inner plates 75 which cooperate with defined in the gear housing 11 outer plates 79 by their axial adjustability such that they can be brought into a frictional contact or from a frictional contact.
  • the electric motor 37 actuates the axial adjustment device 87 provided with a swivel wheel 89 and a ball ramp disk 91 via an idler gear 85 which is driven by its drive shaft 83 and which is connected on one side to the drive shaft 83 of the electric motor 37 and on the other side with the pivot wheel 89 of the means 87 for axial adjustment is engaged.
  • the intermediate gear 85 serves to set a gear ratio between the electric motor 37 and the swing gear 89, which is determined by a number of teeth of the electric motor 37 and a number of teeth of the pivot wheel 89, and for bridging the distance of the electric motor 37 from the longitudinal axis X, wherein the distance is bridged in particular by the diameter of the intermediate gear 85. It is left to the skilled person to use for bridging the distance between the electric motor and the longitudinal axis in addition to the embodiment formed as an intermediate single-stage spur gear according to the particular space conditions also a two-stage or multi-stage spur gear.
  • the ball ramp disk 91 which is mounted so as to be non-rotatable and axially displaceable in the gearbox housing 11, has at least three grooves 93 which vary in their depth over their radius.
  • the grooves 93 of the ball ramp disk 91 corresponding also varying in depth grooves 95 of the pivot wheel 89 are at least three trained as balls 97 rolling elements over which an axial movement of the ball ramp disk 91 results in a caused by the electric motor 37 turning the pivot wheel 89 , so that upon an axial movement in the direction of the Y-axis, the housing-fixed outer disks 79, after overcoming a clearance of the means for axial position 87 with the inner disk 75 of the brake device 51 enter into a frictional engagement.
  • the transfer stage 39 runs around the longitudinal axis X without torque transfer. If a friction connection in the multi-disc brake 77 is triggered via the electric motor 37, a torque vectoring torque acting on the respective output shaft 3 or 5 is generated from the drive torque. This is done by a support of the planet carrier 65 via the brake device 51 in the gear housing 11. It is thus a torque transfer from the drive shaft 2 via the differential cage 19 and from there by means of the planet carrier 65 from the first sun gear 61 to the respective output shaft 3 and 5 connected second sun gear 63 generated by means of which a different torque distribution to the left output shaft 3 and the right Abfriebswelle 5 can be achieved.
  • the brake device 51 is arranged on a region of the transmission stage 39 facing away from the transmission center 8, whereby the braking device 51 is approximately the same distance from the longitudinal axis X as a planetary axis Z and thus advantageously small in size having
  • the multi-disc brake 77 is presently arranged in the direction of the planetary axis Z between the translation stage 39 and the axial actuation device 87 which can be actuated by the motor 37, whereby the swivel wheel 89 of the axial adjustment device 87 is easy to actuate.
  • FIG. 2 shows the gear unit 1 with an alternative arrangement of the brake device 51 'with respect to the gear stage 39 ", wherein the brake device 51' is arranged on a region of the gear stage 39 'facing the gear center 8.
  • the disk brake 77' is corresponding to that in FIG Fig. 1 embodiment shown in the direction of the planetary axis Z between the means 87 'for axial adjustment and the translation stage 39',

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Retarders (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)

Abstract

L'invention concerne une unité de transmission, notamment une unité de transmission à l'essieu arrière, destinée à transmettre un couple d'entraînement d'un arbre d'entrée (2) à deux arbres de sortie (3, 5) au moyen d'une unité de différentiel (15) et d'un dispositif (14) à réglage continu pouvant être actionné par au moins un moteur (37), destiné à influencer le degré de répartition du couple d'entraînement sur les arbres de sortie (3, 5). L'unité de différentiel (15) comporte un différentiel (17) et un carter de différentiel (19) connecté activement à l'arbre d'entrée (2). Le dispositif (14) destiné à influencer le degré de répartition du couple d'entraînement comporte au moins un train planétaire en tant qu'étage de multiplication (39) connecté activement au carter de différentiel (19) et à un arbre de sortie correspondant (3 ou 5), ledit train planétaire présentant un dispositif de freinage (51). Selon l'invention, le dispositif de freinage (51) est disposé de façon latéralement décalée à côté des satellites (69, 71) de l'étage de multiplication (39), en direction d'un axe planétaire (Z), et au moins essentiellement à l'intérieur d'une zone d'extension radiale des satellites (69, 71) autour d'un axe longitudinal (X) des arbres de sortie (3, 5).
EP07729511A 2006-05-30 2007-05-25 Unité de transmission destinée à transmettre un couple d'entraînement d'un arbre d'entrée à deux arbres de sortie Ceased EP2024197A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006025062A DE102006025062A1 (de) 2006-05-30 2006-05-30 Getriebeeinheit zur Führung eines Antriebsmoments von einer Antriebswelle auf zwei Antriebswellen
PCT/EP2007/055082 WO2007138001A1 (fr) 2006-05-30 2007-05-25 Unité de transmission destinée à transmettre un couple d'entraînement d'un arbre d'entrée à deux arbres de sortie

Publications (1)

Publication Number Publication Date
EP2024197A1 true EP2024197A1 (fr) 2009-02-18

Family

ID=38370363

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07729511A Ceased EP2024197A1 (fr) 2006-05-30 2007-05-25 Unité de transmission destinée à transmettre un couple d'entraînement d'un arbre d'entrée à deux arbres de sortie

Country Status (5)

Country Link
US (1) US20090192006A1 (fr)
EP (1) EP2024197A1 (fr)
JP (1) JP2009539044A (fr)
DE (1) DE102006025062A1 (fr)
WO (1) WO2007138001A1 (fr)

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Publication number Priority date Publication date Assignee Title
US20080176702A1 (en) * 2007-01-19 2008-07-24 Showalter Dan J Torque vectoring system
SE533094C2 (sv) * 2008-04-24 2010-06-29 Haldex Traction Ab Torque vectoring-anordning och medel för dess kontroll
DE102010053447A1 (de) * 2010-12-06 2012-06-06 GM Global Technology Operations LLC Antriebseinheit, insbesondere Heckantriebseinheit, für einen Allradantrieb eines Kraftfahrzeuges
DE102010053414A1 (de) 2010-12-06 2012-06-06 GM Global Technology Operations LLC Antriebseinheit, insbesondere Heckantriebseinheit, für einen Allradantrieb eines Kraftfahrzeuges
CN103273841B (zh) * 2013-04-28 2016-02-10 明双奇 后桥省力节能传动装置
DE102013105839B4 (de) * 2013-06-06 2015-04-16 Pierburg Gmbh Betätigungsvorrichtung sowie Klappenvorrichtung mit einer derartigen Betätigungsvorrichtung
CN103692907B (zh) * 2014-01-03 2016-01-27 合肥工业大学 一种电动汽车的动力系统总成
WO2016150411A1 (fr) * 2015-03-20 2016-09-29 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Entraînement d'essieu électrique pour un véhicule automobile

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DE102005003691A1 (de) * 2004-03-08 2005-09-29 Borgwarner Inc., Auburn Hills Variable Differentialanordnung

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JP3067070B2 (ja) * 1993-11-26 2000-07-17 株式会社クボタ トラクタの後車軸ケース装置
JP3103779B2 (ja) * 1996-11-22 2000-10-30 建治 三村 差動装置
JP4116146B2 (ja) * 1998-05-06 2008-07-09 Ｇｋｎ ドライブライン トルクテクノロジー株式会社 デファレンシャル装置
DE10340912B4 (de) * 2003-09-05 2006-04-06 Gkn Driveline International Gmbh Antriebsanordnung
FR2864190B1 (fr) * 2003-12-19 2007-03-02 Peugeot Citroen Automobiles Sa Differentiel asymetrique dissipatif a double train epicycloidal,pour vehicule automobile
US7044880B2 (en) * 2004-05-20 2006-05-16 Magna Powertrain, Inc. Torque distributing differential assembly
US7238140B2 (en) * 2004-07-29 2007-07-03 The Timken Company Differential with torque vectoring capabilities
WO2006074679A1 (fr) * 2004-12-24 2006-07-20 Gkn Driveline International Gmbh Engrenage differentiel
DE102005004290B4 (de) * 2005-01-28 2006-11-02 Gkn Driveline International Gmbh Getriebemodul zur variablen Drehmomentverteilung

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DE102005003691A1 (de) * 2004-03-08 2005-09-29 Borgwarner Inc., Auburn Hills Variable Differentialanordnung

Also Published As

Publication number Publication date
JP2009539044A (ja) 2009-11-12
US20090192006A1 (en) 2009-07-30
WO2007138001A1 (fr) 2007-12-06
DE102006025062A1 (de) 2007-12-06

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