CN111120593A - Pure electric double-gear planetary row driving system - Google Patents

Pure electric double-gear planetary row driving system Download PDF

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Publication number
CN111120593A
CN111120593A CN202010076765.9A CN202010076765A CN111120593A CN 111120593 A CN111120593 A CN 111120593A CN 202010076765 A CN202010076765 A CN 202010076765A CN 111120593 A CN111120593 A CN 111120593A
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China
Prior art keywords
gear
planetary
output
input
sun
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Pending
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CN202010076765.9A
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Chinese (zh)
Inventor
梁欢文
王豫
陈军
段福海
何思杰
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Guangzhou Xinyu Power Technology Co Ltd
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Guangzhou Xinyu Power Technology Co Ltd
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Priority to CN202010076765.9A priority Critical patent/CN111120593A/en
Publication of CN111120593A publication Critical patent/CN111120593A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • 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
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/065—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with a plurality of driving or driven shafts
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/10—Braking arrangements
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H2037/048—Combinations of parallel shaft and orbital motion gearing, wherein the orbital motion gear has more than one connection with the parallel shaft 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a pure electric double-gear planetary gear driving system.A motor drives a double-gear planetary gear, each gear planetary gear consists of an input sun gear, a planetary gear set and an output sun gear, each gear outputs power, and when the power switching of two speed ratios is realized by selecting the closing and releasing of two groups of brakes, the power connection of gear shifting is rapid and smooth; meanwhile, the two sun wheels are respectively responsible for inputting and outputting the power of the planet row, a gear ring with a larger diameter is not needed, the whole vehicle power structure is simple, the loss is low, the transmission efficiency is high, and the driving device is suitable for being applied to a pure electric vehicle driving system.

Description

Pure electric double-gear planetary row driving system
Technical Field
The invention belongs to a vehicle power system, and particularly relates to a driving system for generating double-speed gears by a double-gear planetary gear row based on a coaxial planetary gear set framework.
Background
Energy greening has become the willingness of most countries in the world, more and more countries encourage the development of electric vehicles, and the development of fuel vehicles is limited, at present, the electric vehicles in China mostly adopt a single-stage speed reduction driving scheme no matter in the fields of cars, SUVs, light trucks, buses and the like, but the single-stage speed reduction driving scheme cannot ensure that a driving motor runs in a high-efficiency area under the two conditions of heavy-load starting and highest speed per hour. Adopt two fender variable speed drive scheme on only few motorcycle types on the market, two fender variable speed scheme majority adopt AMT shift fork mode of shifting at present, but its shift is suddenly hindered and is felt seriously, power is interrupted etc. and hinder the problem that is difficult to avoid always.
Disclosure of Invention
The invention aims to solve the technical problem of providing a pure electric double-gear planetary gear drive system which is smooth in gear shifting connection, simple in transmission structure and high in transmission efficiency.
In order to solve the technical problems, the invention adopts the technical scheme that: a pure electric double-gear planetary gear driving system comprises at least one motor, wherein the motor drives double-gear planetary gears, each gear planetary gear consists of an input sun gear, a planetary gear set and an output sun gear, and each gear outputs power through the output sun gear.
Furthermore, the planetary wheel set is composed of a front planet wheel and a rear planet wheel coaxially mounted with the front planet wheel, the front planet wheel is in meshing transmission with the input sun wheel, and the rear planet wheel is in meshing transmission with the output sun wheel.
Further, the motor drives an input sun gear through a gear set, and the output sun gear outputs power through another gear set.
Further, the planetary gear set directly or indirectly transmits a brake.
Further, the planetary gear set directly or indirectly transmits a brake through a coaxially installed rotating arm.
When the technical scheme is implemented, the motor drives the double-gear planetary row of the coaxial planetary gear set, and when the power switching of two speed ratios is realized by selecting the closing and releasing of two groups of brakes, the power connection of gear shifting is rapid and smooth; meanwhile, the two sun wheels are respectively responsible for inputting and outputting the power of the planet row, a gear ring with a larger diameter is not needed, the whole vehicle power structure is simple, the loss is low, the transmission efficiency is high, and the driving device is suitable for being applied to a pure electric vehicle driving system.
Drawings
Fig. 1 is a schematic diagram of a pure electric two-gear planetary gear drive system.
In the figure: 1-motor, 2-main input shaft, 3-first gear, 4-first gear input gear, 5-second gear input gear, 6-first gear input shaft, 7-second gear input shaft, 8-first gear input sun gear, 9-second gear input sun gear, 10-first gear forward planetary gear, 11-second gear forward planetary gear, 12-first gear rear planetary gear, 13-second gear rear planetary gear, 14-first gear output sun gear, 15-second gear output sun gear, 16-first gear brake bull gear, 17-second gear brake bull gear, 18-first gear planetary gear shaft, 19-second gear planetary gear shaft, 20-first gear forward support bearing, 21-second gear forward support bearing, 22-first gear rear support bearing, 23-second gear rear support bearing, 24-first gear tumbler, 25-II gear tumbler, 26-I gear output shaft, 27-II gear output shaft, 28-I gear output gear, 29-II gear output gear, 30-second gear, 31-third gear, 32-I gear brake pinion, 33-II gear brake pinion, 34-I gear shaft, 35-II gear shaft, 36-I gear brake disc, 37-II gear brake disc, 38-I gear brake, 39-II gear brake disc, and 40-total output shaft.
Detailed Description
The following further describes embodiments of the present invention with reference to the drawings. It should be noted that the description of the embodiments is provided to help understanding of the present invention, but the present invention is not limited thereto. In addition, the technical features involved in the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.
As shown in fig. 1, the pure electric double-gear planetary gear drive system mainly comprises a total input shaft, a first gear, two groups of input gears and input shafts thereof, a double-gear planetary gear, two groups of brakes, two groups of output shafts and output gears thereof, a second gear, a third gear and a total output shaft. Each gear planetary row is provided with an input planetary row and an output planetary row, and the two gear planetary rows are arranged in parallel.
The motor 1 is fixedly connected with a main input shaft 2, a first gear 3 is fixedly installed or directly processed on the main input shaft 2, the first gear 3 is simultaneously externally meshed with a first-gear input gear 4 and a second-gear input gear 5, the first-gear input gear 4 is fixedly installed or directly processed on a first-gear input shaft 6, and the second-gear input gear 5 is fixedly installed or directly processed on a second-gear input shaft 7; the second gear 30 and the third gear 31 are fixedly mounted on or directly machined on the main output shaft 40 at the same time, the second gear 30 is externally meshed with the first-gear output gear 28, the third gear 31 is externally meshed with the second-gear output gear 29, the first-gear output gear 28 is fixedly mounted on or directly machined on the first-gear output shaft 26, and the second-gear output gear 29 is fixedly mounted on or directly machined on the second-gear output shaft 27.
The I-gear planetary gear set comprises an I-gear input sun gear 8, an I-gear forward planet gear 10, an I-gear planet gear shaft 18, an I-gear rear planet gear 12, an I-gear output sun gear 14, an I-gear rotating arm 24 and an I-gear braking large gear 16, wherein the I-gear input sun gear 8 is externally engaged with the I-gear forward planet gear 10, the I-gear output sun gear 14 is externally engaged with the I-gear rear planet gear 12, the I-gear forward planet gear 10 and the I-gear rear planet gear 12 are fixedly installed or directly processed on the I-gear planet gear shaft 18, the I-gear planet gear shaft 18 is installed on the I-gear rotating arm 24 through an I-gear forward support bearing 20 and an I-gear rear support bearing 22, the I-gear input sun gear 8 is fixedly installed or directly processed on the I-gear input shaft 6, and the I-gear output sun gear 14 is fixedly installed or; the I-gear braking large gear 16 is fixedly installed or directly processed on the I-gear rotating arm 24, a plurality of I-gear braking small gears 32 are uniformly distributed on the outer circumference of the I-gear braking large gear 16, the I-gear braking small gears 32 are externally meshed with the I-gear braking large gear 16 to form an I-gear shifting gear pair, the I-gear braking small gears 32 are fixedly connected with an I-gear braking disc 36 through an I-gear shaft 34, and the I-gear braking disc 36 is installed between left and right friction blocks of an I-gear brake 38 according to a certain gap.
The second-gear planetary gear set comprises a second-gear input sun gear 9, a second-gear front planetary gear 11, a second-gear planetary gear shaft 19, a second-gear rear planetary gear 13, a second-gear output sun gear 15, a second-gear rotating arm 25 and a second-gear braking large gear 17, wherein the second-gear input sun gear 9 is externally engaged with the first-gear front planetary gear 11, the second-gear output sun gear 15 is externally engaged with the second-gear rear planetary gear 13, the second-gear front planetary gear 11 and the second-gear rear planetary gear 13 are fixedly installed or directly machined on the second-gear planetary gear shaft 19, the second-gear planetary gear shaft 19 is installed on the second-gear rotating arm 25 through a second-gear front supporting bearing 21 and a second-gear rear supporting bearing 23, the second-gear input sun gear 9 is fixedly installed or directly machined on the second-gear input shaft 7, and the second-gear output sun gear 15 is fixedly installed or; the II-gear braking large gear 17 is fixedly installed or directly processed on the II-gear rotating arm 25, a plurality of II-gear braking small gears 33 are evenly distributed on the outer circumference of the II-gear braking large gear 17, the II-gear braking small gears 33 are externally meshed with the II-gear braking large gear 17 to form a II-gear shifting gear pair, the II-gear braking small gears 33 are fixedly connected with an II-gear braking disc 37 through an II-gear shaft 35, and the II-gear braking disc 37 is installed between a left friction block and a right friction block of an II-gear brake 39 according to a certain gap.
The pure electric double-gear planetary row driving system can realize the following five driving modes.
And I-gear driving mode. The first gear brake 38 locks the first gear brake disc 36, the second gear brake 39 releases the second gear brake disc 37, further, the first gear rotating arm 24 is in a locked state, the second gear rotating arm 25 is in a free rotation state, the motor 1 is powered by a vehicle-mounted battery and transmits power to the main input shaft 2, the main input shaft 2 transmits power to the first gear 3, the second gear planetary row does not output power because the second gear rotating arm 25 is in a free rotation state, therefore, the first gear 3 transmits power to the first gear input shaft 6 through the first gear input gear 4, the first gear input shaft 6 transmits power to the first gear input sun gear 8, the first gear input sun gear 8 transmits power to the first gear forward planetary gear 10, the first gear forward planetary gear 10 transmits power to the first gear rear planetary gear 12 through the first gear planetary gear shaft 18, the first gear rear planetary gear 12 transmits power to the first gear output sun gear 14, the first gear output sun gear 14 transmits power to the first gear output gear 28 through the first gear output shaft 26, the first gear output gear 28 transfers power to the main output shaft 40 for output through the second gear 30. The I gear ratio is as follows:
Figure BDA0002378679840000031
n 1: input shaft speed; n 2: the rotation speed of the output shaft; z1: the number of teeth of the first gear 3; z2: the number of teeth of the first-gear input gear 4; z3: the number of teeth of the second-gear input gear 5; z4: the number of teeth of the input sun gear 8 of the first gear; z5: the number of teeth of the input sun gear 9 in gear ii; z6: the number of teeth of the first-gear forward planetary gear 10; z7: the number of teeth of the second-gear forward planetary gear 11; z8: the number of teeth of the first-gear rear planet wheel 12; z9: the number of teeth of the rear planet wheel 13 in the second gear; z10: the number of teeth on the first-gear output sun gear 14; z11: gear II output sun gear 15 tooth number; z12: the number of teeth of the first-gear output gear 28; z13: the number of teeth of the second-gear output gear 29; z14: the number of teeth of the third gear 30; z15: the number of teeth of the fourth gear 31.
And II-gear driving mode. The first gear brake 38 releases the first gear brake disc 36, the second gear brake 39 locks the second gear brake disc 37, further, the second gear rotating arm 25 is in a locked state, the first gear rotating arm 24 is in a free rotation state, the motor 1 is powered by a vehicle-mounted battery to generate power and transmit the power to the main input shaft 2, the main input shaft 2 transmits the power to the first gear 3, the first gear planetary row does not output power because the first gear rotating arm 24 is in the free rotation state, the first gear 3 transmits the power to the second gear input shaft 7 through the second gear input gear 5, the second gear input shaft 7 transmits the power to the first gear input sun gear 9, the second gear input sun gear 9 transmits the power to the second gear forward planetary gear 11, the second gear forward planetary gear 11 transmits the power to the second gear rear planetary gear 13 through the second gear planetary gear shaft 19, the second gear rear planetary gear 13 transmits the power to the second gear output sun gear 15, the second gear output sun gear 15 transmits the power to the second gear output gear 29 through the second gear output, the II-gear output gear 29 transmits power to the total output shaft 40 through the third gear 31 for output. The gear ratio of the second gear is as follows:
Figure BDA0002378679840000041
a braking energy recovery mode. When the whole vehicle is in a first-gear driving mode and is decelerating, braking and sliding, the motor 1 is converted into a power generation mode, the kinetic energy of the whole vehicle is transmitted to the second gear 30 through the main output shaft 40, the second gear 30 transmits the kinetic energy to the first-gear output gear 28, the first-gear output gear 28 transmits the kinetic energy to the first-gear output sun gear 14 through the first-gear output shaft 26, the first-gear output sun gear 14 transmits the kinetic energy to the first-gear rear planet gear 12, the first-gear rear planet gear 12 transmits the kinetic energy to the first-gear front planet gear 10 through the first-gear planet gear shaft 26, the first-gear front planet gear 10 transmits the kinetic energy to the first-gear input sun gear 8, the first-gear input sun gear 8 transmits the kinetic energy to the first-gear input gear 4 through the first-gear input shaft 6, the first-gear input gear 4 transmits the kinetic energy to the first gear 3, the first gear 3 transmits the kinetic energy to the motor 1 through the main input shaft 2 to drive a motor rotor, and the braking energy recovery of the whole vehicle is completed.
When the whole vehicle is in a second-gear driving mode and is decelerating, braking and sliding, the motor 1 is converted into a power generation mode, at the moment, if the speed of the whole vehicle is larger than a preset value, the locking state of a second-gear brake 39 is kept, a first-gear brake 38 is released, the kinetic energy of the whole vehicle is transmitted to a third gear 31 through a main output shaft 40, the kinetic energy is transmitted to a second-gear output gear 29 through the third gear 31, the kinetic energy is transmitted to a second-gear output sun gear 15 through a second-gear output shaft 27 by the second-gear output sun gear 29, the kinetic energy is transmitted to a second-gear rear planet gear 13 by the second-gear output sun gear 15, the kinetic energy is transmitted to a second-gear front planet gear 11 through a second-gear planet gear shaft 19 by the second-gear rear planet gear 13, the kinetic energy is transmitted to a second-gear input sun gear 9 by the second-gear input shaft 7, the second-gear input, the first gear 3 transmits kinetic energy to the motor 1 through the main input shaft 2 to drive a motor rotor to rotate at a high speed, the motor 1 converts the kinetic energy into electric energy which is rectified by a controller and then stored in a vehicle-mounted power supply, and the recovery of the braking energy of the whole vehicle is completed.
When the speed of the whole vehicle is reduced to be smaller than a preset value, the whole vehicle controller sends an instruction to indicate that the second-gear brake 39 is switched to a release state, the first-gear brake 38 is switched to a locking state, and the braking energy recovery process is the same as that in the first-gear driving mode.
A parking mode. I fender brake locking I keep off brake disc, II fender brake locking II keep off brake discs, I fender rocking arm is in the locking state promptly, and II fender rocking arms are in the locking state, therefore, total output shaft 40 is in the locking state, realizes parking mode.
Neutral mode. The first gear brake releases the first gear brake disc and the second gear brake releases the second gear brake disc, namely, the first gear rotating arm is in a free rotating state, the second gear rotating arm is in a free rotating state, the total output shaft 40 is in a free rotating state, and a neutral gear mode is realized.
The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the described embodiments. It will be apparent to those skilled in the art that various changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, and the scope of protection is still within the scope of the invention.

Claims (5)

1. The utility model provides a pure electric two keeps off planet row actuating system, includes an at least motor, its characterized in that: the motor drives the double-gear planetary rows, each gear planetary row is composed of an input sun gear, a planetary gear set and an output sun gear, and each gear outputs power through the output sun gear.
2. The electric-only two-gear planetary gear drive system according to claim 1, characterized in that: the planetary wheel set is composed of a front planetary wheel and a rear planetary wheel coaxially mounted with the front planetary wheel, the front planetary wheel is in meshing transmission with the input sun wheel, and the rear planetary wheel is in meshing transmission with the output sun wheel.
3. The electric-only two-gear planetary gear drive system according to claim 1, characterized in that: the motor is driven by the gear set to input the sun gear, and the output sun gear outputs power by the other gear set.
4. The electric-only two-gear planetary gear drive system according to claim 1, characterized in that: the planetary gear set directly or indirectly drives a brake.
5. The electric-only two-gear planetary gear drive system according to claim 4, characterized in that: the planetary gear set directly or indirectly drives the brake through a rotating arm which is coaxially arranged.
CN202010076765.9A 2020-01-23 2020-01-23 Pure electric double-gear planetary row driving system Pending CN111120593A (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102155521A (en) * 2010-02-11 2011-08-17 宁波宏协离合器有限公司 Planetary gear mechanism and mechanical speed changer comprising same
EP2842781A1 (en) * 2013-08-21 2015-03-04 Volkswagen Aktiengesellschaft Drive assembly for a motor vehicle
CN209666837U (en) * 2018-12-11 2019-11-22 广州汽车集团股份有限公司 Pure electric drive system and automobile
WO2020001589A1 (en) * 2018-06-29 2020-01-02 比亚迪股份有限公司 Transmission, power drive system and vehicle
CN211667108U (en) * 2020-01-23 2020-10-13 广州市新域动力技术有限公司 Pure electric double-gear planetary row driving system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102155521A (en) * 2010-02-11 2011-08-17 宁波宏协离合器有限公司 Planetary gear mechanism and mechanical speed changer comprising same
EP2842781A1 (en) * 2013-08-21 2015-03-04 Volkswagen Aktiengesellschaft Drive assembly for a motor vehicle
WO2020001589A1 (en) * 2018-06-29 2020-01-02 比亚迪股份有限公司 Transmission, power drive system and vehicle
CN209666837U (en) * 2018-12-11 2019-11-22 广州汽车集团股份有限公司 Pure electric drive system and automobile
CN211667108U (en) * 2020-01-23 2020-10-13 广州市新域动力技术有限公司 Pure electric double-gear planetary row driving system

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