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WO2012028372A1 - Unité d'entraînement - Google Patents

Unité d'entraînement Download PDF

Info

Publication number
WO2012028372A1
WO2012028372A1 PCT/EP2011/062071 EP2011062071W WO2012028372A1 WO 2012028372 A1 WO2012028372 A1 WO 2012028372A1 EP 2011062071 W EP2011062071 W EP 2011062071W WO 2012028372 A1 WO2012028372 A1 WO 2012028372A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
planetary
drive unit
differential
sun gear
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
PCT/EP2011/062071
Other languages
German (de)
English (en)
Inventor
Tomas Smetana
Philip Wurzberger
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of WO2012028372A1 publication Critical patent/WO2012028372A1/fr
Anticipated expiration legal-status Critical
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
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with 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
    • F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
    • F16H2048/364—Differential gearings characterised by intentionally generating speed difference between outputs using electric or hydraulic motors

Definitions

  • the invention relates to a drive unit with at least one main motor and a servomotor and with a transmission in which the motors and the main axis of the transmission are aligned coaxially with each other.
  • Such a drive unit is described in DE 10 2008 061 A1.
  • Such drive units have a plurality of individual components, such as gears, planet carriers, engine parts, bearings, etc.
  • the object of the invention is to provide a drive unit which is compact and accordingly requires little space for itself and which can be easily assembled.
  • the drive unit has at least one main motor and a servomotor and a transmission.
  • the motors are preferably electric motors.
  • the axes of rotation of the rotor shafts and the main axis of the gear are aligned coaxially with each other.
  • the motors and gearbox are housed in a common housing.
  • the transmission is formed at least of a differential and a torque vectoring unit.
  • the differential is drivable with the main motor and the torque vectoring unit connected between the differential and the servomotor is drivably operatively connected to the servomotor.
  • the common same housing of the individual modules in a housing allows a compact and independent drive unit.
  • the term torque vectoring unit stands for a gearbox, preferably for a planetary gearbox, over which power applied by the servo motor is introduced into the differential torque in addition to the main drive.
  • the drive unit can be mounted easily if, as an embodiment of the invention provides, at least the differential is an independent of the housing in self-holding preassembled unit that can be used in the housing or in a housing part. With such a design, the number of parts at the location of the final assembly of the drive unit is reduced.
  • the torque-vectoring unit is a preassembled unit that is self-contained independently of the housing.
  • a further embodiment of the invention provides that the drive unit has a housing formed from at least three housing parts, in which preferably the main motor, the gearbox and the servo motor are each housed in another of the housing parts.
  • FIG. 1 shows a drive unit 1 in a longitudinal section along the main axis 9.
  • the drive unit 1 is an independent compact unit in which a main motor 2, a transmission 3, which consists of a differential 4 and of a torque vectoring unit 5 , a servomotor 6, a first output shaft 7 and a second output shaft 8 with respect to their main axes 9 (axes of rotation of the rotors and axes of symmetry of the sun) are arranged in a common housing 10 coaxial or concentric with each other.
  • the housing 10 is formed in three parts.
  • a middle housing part 101 receives the transmission 3 and is left and right to the motors 2 and 6 open.
  • a left housing part 102 the main motor 2 and a sensor 12 are installed.
  • the sensor 12 sits on the left side of the left housing part 102, is closed to the outside with a lid 121 and sealed with an O-ring 125.
  • the lid 121 has a concentric to the main axis circular cylindrical hole 122 with sealing seat 124, in which a seal 123 is seated.
  • the left housing part 102 is closed on the right to the gearbox 3 with a first intermediate wall 104, which has a first feedthrough 105 concentric to the main axis 9.
  • a concentric to the main axis 9 second passage 106 in the left housing part 102 is the first passage 105 by far with coaxial.
  • the second drive 6 and a further sensor 12 are seated in a right-hand housing part 103.
  • the sensor 12 is seated on the right-hand housing part 103 on the right-hand side and is closed off to the outside with a cover 121 and sealed with an O-ring 125.
  • the lid 121 has a concentric to the main axis circular cylindrical hole 122 with sealing seat 124, in which a seal 123 is seated.
  • the right-hand housing part 103 is closed on the left toward the transmission 3 with a second intermediate wall 107, which has a third passage 108 concentric with the main axis 9.
  • a concentric to the main axis 9 fourth passage 109 is the third passage 108 with axial distance coaxially opposite.
  • the output shaft 7 and the output shaft 8 are inserted concentrically to the main axis 9 centrally in the passages 105 to 109.
  • the intermediate walls 104 and 107 each have an annular flange 1 1, which is provided with circumferentially adjacent internal thread holes 1 11 and circumferentially adjacent through holes 112 in sealing surfaces 1 15.
  • On the front side of the respective open side of the housing parts 102 and 103 are in each case a sealing surface 1 13 circumferentially adjacent through holes 1 14 introduced introduced the bolt circle with the bolt circle of the internal threaded holes 1 11 in the sealing surface 115 of the respective annular flange 1 1.
  • the central housing part 101 has frontally in sealing surfaces 1 17 introduced internal threaded holes 1 18, whose bolt circle with the bolt circle of the through-holes 112 in the annular flange 1 corresponds.
  • the intermediate walls 104 and 107 are connected to the respective left housing part 102 and right housing part 103 by means of screws 16.
  • the sealing surfaces are 1 13 of the respective housing part 102 and 103 frontally to a sealing surface 1 15 at.
  • the screws 1 16 pass through one of the through holes 14 and are screwed into the internal threaded holes 1 1 1.
  • the housing parts 102 and 103 are each connected via one of the intermediate walls 104 or 107 with the central housing part 101.
  • the sealing surfaces 1 15 and 1 17 face each other.
  • the screws 1 19 pass through one of the through holes 112 of the annular flange 1 1 and are screwed into the internal threaded holes 1 18 of the central housing part 101.
  • FIG. 2 shows the longitudinal section through the drive unit according to FIG. 2.
  • a first rotor shaft 20 of the main motor 2 is connected in a rotationally fixed manner to a first sun gear 40 of the differential 4 about the rotor axis 9 or main axis 9.
  • the main motor 2 is coupled via the first rotor shaft 20 with the first sun gear 40, which is a first power input 30 of the transmission 3, transmission technology.
  • the first rotor shaft 20 and the first Sun gear 40 are rotatably supported by means of the first ball bearing 21 and the second ball bearing 22.
  • the ball bearings 21 and 22 are against each other employed angular contact ball bearings and sitting in the left housing part 102 in the passages 105 and 106.
  • Differential shafts of the differential 4 are a second sun gear 41 and a third sun gear 42nd
  • the first sun gear 41 is non-rotatably mounted on the first output shaft 7 about the main axis 9.
  • the first rotor shaft 20 is a hollow shaft in which the first output shaft 7 is rotatably supported by a first needle bearing 23 and by a second needle bearing 24.
  • the shank 401 of the first sun gear 40 extends axially partially into the rotor shaft 20 as far as the second needle bearing 24.
  • the second sun gear 42 is non-rotatably mounted on the second output shaft 8 about the main axis 9.
  • the second output shaft 8 is rotatably supported about the main axis 9 by means of a third needle bearing 63 and a fourth needle bearing 64 in a second rotor shaft 60 of the servo motor designed as a hollow shaft.
  • the second rotor shaft 60 is rotatably mounted by means of a third ball bearing 61 and a fourth ball bearing 62 rotatably in the bushings 108 and 109 in the right housing part 103.
  • the ball bearings 61 and 62 are against each other employed angular contact ball bearings.
  • the second rotor shaft 60 protrudes axially out of the servomotor 6 concentrically with the main axis 9 into the torque vectoring unit 5.
  • a fourth sun gear 50 sits around the main shaft 9 rotationally fixed on the second rotor shaft 60.
  • the servomotor 6 is coupled by means of the fourth sun gear 50 with the gearbox 3 transmission technology.
  • the torque vectoring unit 5 and the Differenzia! 4 are geared technically coupled via a first ring gear 51 of the torque-vectoring unit 5 and first planet wheels 43 of the differential 4.
  • Figures 3 and 3a Figure 3 shows the integrated into the drive unit 1
  • FIG. 3a shows the differential 4 as a preassembled and self-sustaining assembly 490.
  • the differential 4 has three planetary gear sets and a lubricating device 13.
  • a first planetary gear set which is connected between the main motor 2 and the actual differential 4, has second planet gears 44, which mesh with the first sun gear 40 and a second ring gear 45 and which together with the lubricating device 13 form part of the assembly 490.
  • the first sun gear 40 and the second ring gear 45 are not part of the assembly 490.
  • the second ring gear 45 is held stationary on the central housing part 101.
  • the second planet gears 44 are each rotatably mounted on first planet pins 442 by means of first planet bearings 441.
  • the first planet pins 442 are each fixed to a first planet carrier 46.
  • the first planet carrier 46 of the differential 4 is formed of four carrier segments 461, 462, 463 and 464 and rotatable about the main axis 9.
  • the carrier segments 461, 462, 463 and 464 are connected to one another in a rotationally fixed manner to the planet carrier 46 and together or in cooperation with the planet pins 481 and 442 hold together the elements of the differential 4 and further elements to form the assembly 490.
  • the first planet pins 442 are each held at three bearing points 443, 444 and 445 in the first planet carrier 46, each of which is formed on one of the support segments 461, 462 and 463.
  • the second planetary gearset is a planetary gearset of the differential 4 and has long third planetary gears 47 meshing with the second sun gear 41 and fourth planetary gears 48.
  • the third planetary gears 47 are rotatably mounted on the first planetary pin 442 between the carrier segments 463 and 464 as well as the second planetary gears 44.
  • the third planetary gear set is formed by the fourth planetary gears 48 meshing with the third planetary gears 47 and the third sun gear 42 and mounted on a second planetary pin 481.
  • the second planetary pin 481 is supported at two bearing points 482 and 483 of the carrier segments 462 and 464.
  • the fourth planetary gear set is formed by the first planetary gears 43 meshing with the first ring gear 51 and a fifth sun gear 52.
  • First ring gear 51 and fifth sun gear 52 are not part of the pre-assembled assembly 490.
  • the first planetary gears 43 are rotatably connected about the planetary axis 485 with a shaft 484 of the fourth planetary gears 48 and rotatable with these on the second planetary pin 481 between the carrier segments 463rd and 464 stored in the assembly 490.
  • Figures 4 and 4a Figure 4 shows the integrated into the drive unit
  • the torque vectoring unit 5 as a detail of the illustration according to FIG. 1 and FIG. 4 a shows the torque vectoring unit 5 as a preassembled and self-holding unit 590.
  • the torque vectoring unit 5 has a housing 53 with a third ring gear 531.
  • the first ring gear 51 of the differential 4 is also integrated in the housing 53.
  • the ring gears 51 and 531 are fixed to the housing held in the housing 53.
  • the housing can also be formed integrally with the ring gears by the teeth of the ring gears are introduced into the housing.
  • the housing 53 is rotatably mounted with a ball bearing 25 radially on a fixed to the right housing part 103 sixth sun gear 532.
  • a second planet carrier 54 is centered on a shaft 533 of the housing 53 to the main axis 9.
  • the second planet carrier 54 is formed from two carrier segments 541 and 542.
  • Third planet pins 56 are received on both sides and on each side in one of the carrier segments 541 and 542.
  • Fifth planetary gears 57 and sixth planetary gears 58 are rotatably mounted in pairs next to one another by means of planetary bearings 571 and 581, respectively, on the third planetary pin 56.
  • a fourth ring gear 55 concentrically seated in the housing 53 is centered on the fifth sun gear 52, which is rotatably mounted on a shaft 421 of the third sun gear 42, and is bolted to this rotatably.
  • the fifth sun gear 52 actually belongs to the fourth planetary gear set of the differential 4 and is in meshing engagement with the assembled drive unit but first planetary gears 43, but is part of the assembly 590.
  • the first planetary gears 43 are in mesh with the first ring gear 51.
  • the fifth planet gears 57 mesh with the fourth sun gear 50 and the fourth ring gear 55.
  • the sixth planet gears 58 mesh with the sixth sun gear 532 and mesh with the third ring gear 531.
  • the sixth sun gear 532 is meshed with the second sun gear 532 Partial wall 107 screwed and therefore not part of the pre-assembled unit 590.
  • FIG. 5 shows schematically and not to scale the structure of the drive unit 1.
  • the rotor 201 of the main motor 2 is connected to the first sun gear 40 via the first rotor shaft 20.
  • Rotor 201, rotor shaft 20 and first sun gear 40 are rotatable relative to the housing 10 about the main axis 9.
  • the first sun gear 40 meshes with second planetary gears 44.
  • the second planet gears 44 are in meshing engagement with the second ring gear 45 and are rotatably mounted about the first pin axis 446 of the first planetary pin 442 rotatably on a respective first planetary pin 442.
  • the first ring gear 51 is fixed to the housing 10.
  • the first planet pins 442 are fixed parallel to the main axis 9 and with the radius A to the main axis 9 on the first planet carrier 46.
  • the first planet carrier 46 is rotatably mounted about the main axis 9 relative to the housing 10.
  • a third planetary gear 47 is rotatably supported respectively with the radius A to the main axis about the first pin axis 446 and relative to the second planetary gears 44.
  • Each of these so-called long planetary gears 47 extends in the axial direction via the second sun gear 41 and the third sun gear 42, each third planetary gear 47 is in meshing engagement with the second sun gear 41 and one of the fourth planetary gears 48.
  • the third planet gears 47 are arranged without contact.
  • the fourth planet gears 48 each rotatable about the pin axis 485 rotatably connected to a first planetary gear 43 and rotatably mounted together with this on each of a second planetary pin 481.
  • the second planet pins 48 like the first planet pins 442, are fixed with their pin axis 446 with the radius A of their pin axis 485 to the main axis 9 on the first planet carrier 46.
  • the fourth planet gears 48 mesh with the third sun gear 42.
  • the first planet gears 43 are meshed with the first ring gear 51 and the fifth sun gear 52, respectively.
  • the first ring gear 51 is rotatably held on the housing 53.
  • the housing 53 is rotatably supported rotatably on the sixth sun gear 532 relative to the housing 10 and relative to the sixth sun gear 532.
  • the sixth sun gear 532 is fixed to the housing 10.
  • the fifth sun gear 52 is fixedly connected to the fourth ring gear 55 and rotatably supported with the ring gear 55 relative to the housing 10.
  • the fourth ring gear 55 is in meshing engagement with the fifth planetary gears 57.
  • the fifth planetary gears 57 are rotatably mounted about the pin axis 561 rotatably mounted on the third planetary pin 56.
  • the third planetary pin 56 are spaced as well as the first planetary pin with its pin axis 446 and the second planetary pin 481 with its pin axis 485 with the radius A of its pin axis 561 to the main axis 9.
  • the third planet pins 56 are fixed on both sides to the second planet carrier 54.
  • the second planet carrier 54 is rotatably mounted relative to the housing 53 rotatably mounted on the housing 10 fixed sixth sun gear 532.
  • the fifth planet gears 57 mesh with the fourth sun gear 50, which is non-rotatably connected to the second rotor shaft 60 of the servomotor 6 and is relatively rotatable relative to the housing 10.
  • the sixth planetary gears 58 are mounted rotatably about the pin axis 485 and relative to the fifth planetary gears 57 on the third planetary pin 56.
  • the sixth planet gears 58 mesh with the sixth sun gear 532 and mesh with the third ring gear 531.
  • the sixth sun gear is bolted to the second diaphragm 107 and thus supported on the housing 10.
  • the third ring gear 531 is like the first ring gear 51 fixed to the housing 53 and rotatable relative to the housing 10 with this.
  • the second sun gear 41 is rotatably supported relative to the first sun gear 40 about the main axis 9 in the hollow first rotor shaft 20 and rotatably connected to the first output shaft 7.
  • the third sun gear 42 is rotatably mounted relative to the first sun gear 40 and the second rotor shaft 60 of the rotor 601 in the form of a hollow shaft second rotor shaft 60 and rotatably connected to the second output shaft 8.
  • Ring flange 51 first ring gear

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne une unité d'entraînement (1) comportant au moins un moteur principal (2) ainsi qu'un servomoteur (6) et une transmission (3), les moteurs (2, 6) et l'axe principal (9) de la transmission (3) étant orientés coaxialement les uns par rapport aux autres et les moteurs (2, 6) et la transmission (3) étant logés dans un carter commun (10). La transmission (3) est constituée d'au moins un différentiel (4) et d'une unité de vectorisation du couple (5), le différentiel (4) est en liaison active d'entraînement avec le moteur principal (2) de même que l'unité de vectorisation du couple (5) montée entre le différentiel (4) et le servomoteur (6) est en liaison active d'entraînement avec le servomoteur (6).
PCT/EP2011/062071 2010-09-03 2011-07-14 Unité d'entraînement Ceased WO2012028372A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010036241 DE102010036241A1 (de) 2010-09-03 2010-09-03 Antriebseinheit
DE102010036241.7 2010-09-03

Publications (1)

Publication Number Publication Date
WO2012028372A1 true WO2012028372A1 (fr) 2012-03-08

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ID=44512399

Family Applications (1)

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PCT/EP2011/062071 Ceased WO2012028372A1 (fr) 2010-09-03 2011-07-14 Unité d'entraînement

Country Status (2)

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DE (1) DE102010036241A1 (fr)
WO (1) WO2012028372A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015039610A1 (fr) * 2013-09-22 2015-03-26 格源动力有限公司 Moteur coaxial comportant un levier de vitesse
CN104812603A (zh) * 2012-07-13 2015-07-29 舍弗勒技术股份两合公司 具有两挡传动装置的电动车桥
US9334942B2 (en) 2013-04-17 2016-05-10 Kabushiki Kaisha Toyota Chuo Kenkyusho Drive torque distribution apparatus
CN104661844B (zh) * 2012-07-13 2017-09-08 舍弗勒技术股份两合公司 用于电动车桥的支承设计
US20180306294A1 (en) * 2017-04-21 2018-10-25 Jilin University Electric differential with torque vectoring function
DE102018213256A1 (de) * 2018-08-08 2020-02-27 Zf Friedrichshafen Ag Anordnung und Verfahren zum Antreiben eines Fahrzeugs
WO2024046852A1 (fr) * 2022-09-01 2024-03-07 Mercedes-Benz Group AG Système d'entraînement électrique pour véhicule à moteur, en particulier pour une automobile, et procédé de fonctionnement dudit système d'entraînement électrique

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20150004374A (ko) * 2012-04-27 2015-01-12 보그워너 토크트랜스퍼 시스템즈 아베 전기 차축
DE102014201322A1 (de) * 2014-01-24 2015-07-30 Siemens Aktiengesellschaft Drehzahlveränderliche elektrische Maschine
DE102014201324A1 (de) * 2014-01-24 2015-07-30 Siemens Aktiengesellschaft Drehzahlveränderliche Maschinen-Getriebe-Einheit
US9511661B2 (en) 2015-03-12 2016-12-06 Deere & Company Driven wheel unit including an axially compact two-speed planetary gear drive assembly
DE102015223130B4 (de) * 2015-11-24 2020-02-06 Schaeffler Technologies AG & Co. KG Antriebseinrichtung mit einem Differentialgetriebe und einer Torque-Vectoring-Einheit
DE102015223131A1 (de) * 2015-11-24 2017-05-24 Schaeffler Technologies AG & Co. KG Antriebseinrichtung für ein Kraftfahrzeug

Citations (5)

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DE4236124A1 (de) * 1991-10-24 1993-05-13 Aisin Aw Co Elektrofahrzeug
AT6549U1 (de) * 2002-09-03 2003-12-29 Magna Steyr Powertrain Ag & Co Antriebsachse für ein kraftfahrzeug mit variabler momentenverteilung
DE102004024086A1 (de) * 2004-05-14 2005-12-08 Audi Ag Antriebsvorrichtung für Kraftfahrzeuge
DE102009003388A1 (de) * 2008-01-25 2009-08-13 Ford Global Technologies, LLC, Dearborn Antriebseinheit für ein Elektro-Hybridfahrzeug
DE102008061946A1 (de) 2008-12-12 2010-06-17 Schaeffler Kg Elektrische Antriebseinheit mit variabler Momentenverteilung

Family Cites Families (1)

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Publication number Priority date Publication date Assignee Title
DE102008061120A1 (de) 2008-12-09 2010-06-10 Suspa Holding Gmbh Spindelaktor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4236124A1 (de) * 1991-10-24 1993-05-13 Aisin Aw Co Elektrofahrzeug
AT6549U1 (de) * 2002-09-03 2003-12-29 Magna Steyr Powertrain Ag & Co Antriebsachse für ein kraftfahrzeug mit variabler momentenverteilung
DE102004024086A1 (de) * 2004-05-14 2005-12-08 Audi Ag Antriebsvorrichtung für Kraftfahrzeuge
DE102009003388A1 (de) * 2008-01-25 2009-08-13 Ford Global Technologies, LLC, Dearborn Antriebseinheit für ein Elektro-Hybridfahrzeug
DE102008061946A1 (de) 2008-12-12 2010-06-17 Schaeffler Kg Elektrische Antriebseinheit mit variabler Momentenverteilung

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104812603A (zh) * 2012-07-13 2015-07-29 舍弗勒技术股份两合公司 具有两挡传动装置的电动车桥
CN104661844B (zh) * 2012-07-13 2017-09-08 舍弗勒技术股份两合公司 用于电动车桥的支承设计
CN104812603B (zh) * 2012-07-13 2018-03-02 舍弗勒技术股份两合公司 具有两挡传动装置的电动车桥
US9334942B2 (en) 2013-04-17 2016-05-10 Kabushiki Kaisha Toyota Chuo Kenkyusho Drive torque distribution apparatus
WO2015039610A1 (fr) * 2013-09-22 2015-03-26 格源动力有限公司 Moteur coaxial comportant un levier de vitesse
US20180306294A1 (en) * 2017-04-21 2018-10-25 Jilin University Electric differential with torque vectoring function
US10663051B2 (en) * 2017-04-21 2020-05-26 Jilin University Electric differential with torque vectoring function
DE102018213256A1 (de) * 2018-08-08 2020-02-27 Zf Friedrichshafen Ag Anordnung und Verfahren zum Antreiben eines Fahrzeugs
WO2024046852A1 (fr) * 2022-09-01 2024-03-07 Mercedes-Benz Group AG Système d'entraînement électrique pour véhicule à moteur, en particulier pour une automobile, et procédé de fonctionnement dudit système d'entraînement électrique

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