Vehicle and dual motor electric drive assembly thereof

Abstract

A vehicle and a dual motor electric drive assembly thereof, the dual motor electric drive assembly including a first drive mechanism and a second drive mechanism located on the same transaxle, the first drive mechanism including a first motor, a first planetary gear mechanism, and a first driver shaft connected in sequence, and the second drive mechanism including a second motor, a second planetary gear mechanism, and a second driver shaft connected in sequence, wherein the first planetary gear mechanism and the second planetary gear mechanism have different structures. The dual motor electric drive assembly has low noise during operation.

Description

[Technical Field]

[0001] [CROSS-REFERENCE TO RELATED APPLICATIONS] This patent application claims priority to Chinese patent application No. 202211679016.0, filed on December 26, 2022, entitled "Automobile and Dual-Motor Electric Drive Assembly Thereof," and Chinese patent application No. 2022116904231, filed on December 27, 2022, entitled "Automobile and Dual-Motor Electric Drive Assembly Thereof," the disclosures of which are incorporated herein by reference in their entirety.

[0002] TECHNICAL FIELD This disclosure relates to the art of electric vehicles, and more particularly to a vehicle and its dual motor electric drive assembly. [Background technology]

[0003] Currently, with the development of the new energy automobile industry, electric vehicles have become a development trend. While the performance of electric vehicles is receiving increasing attention, limitations imposed by the development of motor technology mean that current electric drive assemblies using a single motor to achieve high power output require significant increases in volume and weight, limiting the development of high-performance electric vehicles. Furthermore, as consumers increasingly focus on performance, there is a growing demand for power configurations such as vector control and differential lock. To achieve these functions, single-motor transmission system solutions require the addition of numerous mechanical mechanisms, making it impossible to reduce the volume and weight of the single-motor assembly.

[0004] Therefore, the dual-motor electric drive assembly solution, which uses two motors and corresponding transmission systems to meet the requirements of high-performance electric vehicles, is attracting more and more attention. In addition, since each motor is equipped with a transmission system, the layout of the entire power train becomes more flexible and the two systems can be distributed.

[0005] However, related art dual motor electric drive assemblies have overlapping orders and are noisier than single motor electric drive assemblies, leading to reduced NVH (Noise, Vibration, Harshness) performance of the vehicle. Summary of the Invention [Problem to be solved by the invention]

[0006] The following is a summary of the subject matter described in detail herein. This summary does not limit the scope of the claims. [Means for solving the problem]

[0007] In order to solve the technical problem of the dual motor electric drive assembly that is noisy during operation, the present application provides a dual motor electric drive assembly, comprising: a first drive mechanism and a second drive mechanism; the first drive mechanism includes a first motor, a first planetary gear mechanism, and a first driver shaft connected in sequence; the second drive mechanism includes a second motor, a second planetary gear mechanism, and a second driver shaft connected in sequence; Here, the first planetary gear mechanism and the second planetary gear mechanism have different structures to provide a dual motor electric drive assembly.

[0008] In the technical solution of the present application, the first planetary gear mechanism and the second planetary gear mechanism have different structures, resulting in separate gear orders. This prevents overlapping of the gear orders between the first planetary gear mechanism and the second planetary gear mechanism. This significantly reduces the order noise when the first planetary gear mechanism and the second planetary gear mechanism operate simultaneously, improving the vehicle's NVH performance and providing a more comfortable ride. Furthermore, the first and second motors can be low-power motors. When the first and second motors operate simultaneously, the dual-motor electric drive assembly can output high power, meeting the high-power requirements of the vehicle. Because the first and second motors can be controlled independently, the power output of one or both motors can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control of the vehicle to be realized with more precise control. For example, by controlling the rotation speed and torque of the first and second motors, differential speed and torque distribution between the wheels can be achieved, enabling the vehicle to travel in a straight line.

[0009] The present application also includes a first drive mechanism and a second drive mechanism, the first drive mechanism includes a first motor, a first gear transmission mechanism, and a first driver shaft, which are connected in sequence to be able to transmit power; the second drive mechanism includes a second motor, a second gear transmission mechanism, and a second driver shaft, which are connected in sequence to be able to transmit power; Here, there is provided another dual motor electric drive assembly in which the gears of the first gear transmission mechanism and the gears of the second gear transmission mechanism are arranged so as to be symmetrical in position, and at least two gears arranged symmetrically to each other have different numbers of teeth.

[0010] In the technical solution of the present application, at least two gears arranged symmetrically in the first gear transmission and the second gear transmission have different numbers of teeth, so that the first gear transmission and the second gear transmission are not completely identical, and the orders of the first gear transmission and the second gear transmission are separated, thereby avoiding overlapping orders of the first gear transmission and the second gear transmission. This significantly reduces order noise when the first gear transmission and the second gear transmission operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride. Furthermore, the first motor and the second motor can be low-power motors. When the first motor and the second motor operate simultaneously, the dual-motor electric drive assembly can output high power, meeting the high-power requirements of the vehicle. The first motor and the second motor can be controlled independently, allowing the power output of one or both sides to be changed according to power requirements, thereby realizing functions such as a differential, differential lock, and vector control in the vehicle and providing more accurate control. For example, by controlling the rotation speed and torque of the first motor and the second motor, differential speed and torque distribution between the wheels can be achieved, allowing the car to move in a straight line.

[0011] The present application also includes a first drive mechanism and a second drive mechanism located on the same transaxle, the first drive mechanism includes a first motor, a first planetary gear mechanism, and a first driver shaft connected in sequence; the second drive mechanism includes a second motor, a second planetary gear mechanism, and a second driver shaft connected in sequence; The gears of the first planetary gear set and the second planetary gear set are arranged differently to provide another dual motor electric drive assembly.

[0012] In the technical solution of the present application, the gears of the first gear transmission mechanism and the second gear transmission mechanism are arranged in different ways, so the first gear transmission mechanism and the second gear transmission mechanism are not completely identical, and the orders of the first gear transmission mechanism and the second gear transmission mechanism are separated, thereby avoiding overlapping of the orders of the first gear transmission mechanism and the second gear transmission mechanism, and significantly reducing the order noise when the first gear transmission mechanism and the second gear transmission mechanism operate simultaneously, improving the NVH performance of the automobile and providing a better ride comfort.

[0013] The present application also proposes a vehicle including the dual motor electric drive assembly described above. [Effects of the Invention]

[0014] Other features and advantages of the present application will be set forth in the description that follows, and in part will be obvious from the description, or may be learned by the practice of the present application. Other advantages of the present application may be realized by the techniques described in this specification and the accompanying drawings.

[0015] Other aspects will become apparent upon reading and understanding the accompanying drawings and detailed description. [Brief explanation of the drawings]

[0016] [Figure 1] FIG. 1 is a schematic diagram of a dual motor electric drive assembly according to a first embodiment of the present application. [Figure 2] FIG. 10 is a schematic diagram of a dual motor electric drive assembly in accordance with a second embodiment of the present application. [Figure 3] FIG. 10 is a schematic diagram of a dual motor electric drive assembly in accordance with a third embodiment of the present application. [Figure 4] FIG. 10 is a schematic diagram of a dual motor electric drive assembly in accordance with Example 4 of the present application. [Figure 5] FIG. 10 is a schematic diagram of a dual motor electric drive assembly in accordance with Example 5 of the present application. [Figure 6] FIG. 10 is a schematic diagram of a dual motor electric drive assembly in Example 6 of the present application. [Figure 7]FIG. 10 is a schematic diagram of a dual motor electric drive assembly in accordance with Example 7 of the present application. [Figure 8] FIG. 10 is a schematic diagram of a dual motor electric drive assembly in Example 8 of the present application. [Figure 9] FIG. 10 is a schematic diagram of a dual motor electric drive assembly in Example 9 of the present application. [Figure 10] FIG. 16 is a schematic diagram of a dual motor electric drive assembly in accordance with Example 10 of the present application. DETAILED DESCRIPTION OF THE INVENTION

[0017] Example 1 As shown in Figure 1, Figure 1 illustrates the structure of a dual motor electric drive assembly 100 in Example 1. The dual motor electric drive assembly 100 is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a pure electric vehicle.

[0018] The dual motor electric drive assembly 100 includes a first drive mechanism 1 and a second drive mechanism 2. The first drive mechanism 1 and the second drive mechanism 2 may be mounted on the same transaxle.

[0019] The first drive mechanism 1 includes a first motor 11, a first planetary gear mechanism 12, and a first driver shaft 13. The first planetary gear mechanism 12 is provided between the first driver shaft 13 and the first motor 11. A main shaft of the first motor 11 is connected to the first planetary gear mechanism 12, which is connected to the first driver shaft 13. The first planetary gear mechanism 12 may be a reducer, and the first planetary gear mechanism 12 can increase the torque output by the first motor 11 by reducing the speed before sending it to the first driver shaft 13 to rotate the first driver shaft 13.

[0020] The second drive mechanism 2 includes a second motor 21, a second planetary gear mechanism 22, and a second driver shaft 23. The second planetary gear mechanism 22 is provided between the second driver shaft 23 and the second motor 21. A main shaft of the second motor 21 is connected to the second planetary gear mechanism 22, and the first planetary gear mechanism 12 is connected to the second driver shaft 23. The second planetary gear mechanism 22 may be a reducer, and the second planetary gear mechanism 22 can increase the torque output by the second motor 21 by reducing the speed before sending it to the second driver shaft 23 to rotate and drive the second driver shaft 23. The first motor 11 and the second motor 21 are provided between the first planetary gear mechanism 12 and the second planetary gear mechanism 22, the first driver shaft 13 is provided on the side of the first planetary gear mechanism 12 opposite the second planetary gear mechanism 22, and the second driver shaft 23 is provided on the side of the second planetary gear mechanism 22 opposite the first planetary gear mechanism 12. The first driver shaft 13, the second driver shaft 23, the main shaft of the first motor 11, and the main shaft of the second motor 21 are provided coaxially. The first planetary gear mechanism and the second planetary gear mechanism have different structures.

[0021] Because the first planetary gear mechanism 12 and the second planetary gear mechanism 22 have different structures, their orders are separated and overlapping is avoided. This significantly reduces the order noise when the first planetary gear mechanism 12 and the second planetary gear mechanism 22 operate simultaneously, improving the vehicle's NVH performance and providing a more comfortable ride. Furthermore, the first motor 11 and the second motor 21 can be low-power motors. When the first motor 11 and the second motor 21 operate simultaneously, the dual-motor electric drive assembly 100 can output high power, meeting the high-power requirements of vehicles. Because the first motor 11 and the second motor 21 can be controlled independently, the power output of one or both motors can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control for the vehicle and providing more accurate control. For example, by controlling the rotation speed and torque of the first motor 11 and the second motor 21, differential speed and torque distribution between the wheels can be achieved, allowing the car to travel in a straight line.

[0022] In one exemplary embodiment, the gears of the first planetary gear set 12 and the gears of the second planetary gear set 22 are arranged to be positionally symmetrical, and this positional symmetry is positional mirror symmetry, i.e., for every gear of the first planetary gear set 12, there is a positionally symmetrical gear in the second planetary gear set 22. The first motor 11 and the second motor 21 are connected to two gears of the first planetary gear set 12 and the second planetary gear set 22, respectively, which are positionally asymmetrical to each other.

[0023] The gears of the first planetary gear mechanism 12 and the gears of the second planetary gear mechanism 22 are arranged symmetrically, thereby balancing the forces acting on both opposing sides of the vehicle. Meanwhile, the first motor 11 and the second motor 21 are connected to two gears of the first planetary gear mechanism 12 and the second planetary gear mechanism 22, respectively, that are not symmetrically positioned, and power is input from gears at different positions in the first planetary gear mechanism 12 and the second planetary gear mechanism 22, with the first planetary gear mechanism 12 and the second planetary gear mechanism 22 having different power transmission paths, which further reduces harmonic noise when the first planetary gear mechanism 12 and the second planetary gear mechanism 22 operate simultaneously, improving the NVH performance of the vehicle.

[0024] In one exemplary embodiment, the first planetary gear mechanism 12 is configured as a single-row planetary gear mechanism. The first planetary gear mechanism 12 includes a first sun gear 121, a first planetary gear 122, a first inner ring gear 123, a first planet carrier 124, and a sun gear rotation shaft 120. The first inner ring gear 123 is provided coaxially with the main shaft of the first motor 11. The first inner ring gear 123 includes a connecting member 1232 and a ring gear body 1231. The ring gear body 1231 is configured as a ring. The connecting member 1232 is provided at an end of the ring gear body 1231 closer to the first motor 11. The connecting member 1232 connects the ring gear body 1231 to the main shaft of the first motor 11. The sun gear rotation shaft 120 is provided within the ring gear body 1231 and is provided coaxially with the first inner ring gear 123. The first sun gear 121 is disposed within the first inner ring gear 123, is disposed coaxially with the first inner ring gear 123, and is fixedly fitted to the sun gear rotation axis 120. The first sun gear 121 cannot rotate around the sun gear rotation axis 120. An annular gap exists between the first sun gear 121 and the first inner ring gear 123. The first planetary gears 122 are disposed within the annular gap between the first sun gear 121 and the first inner ring gear 123. The axis of the first planetary gears 122 is parallel to the axis of the first sun gear 121.

[0025] The first sun gear 121 and the first inner ring gear 123 both mesh with the first planetary gears 122. A plurality of first planetary gears 122, for example, three, may be provided, and the plurality of first planetary gears 122 are evenly distributed in the circumferential direction of the first sun gear 121. The first planet carrier 124 includes a first holder 1241 and a first rotating shaft 1242. The first holder 1241 is provided on the side of the first sun gear 121 opposite to the first motor 11. The first rotating shaft 1242 is parallel to the axis of the first sun gear 121, and one end of the first rotating shaft 1242 is connected to the first holder 1241. The number of first rotating shafts 1242 is the same as the number of first planetary gears 122, and the first rotating shafts 1242 are provided in one-to-one correspondence with the first planetary gears 122, and the first planetary gears 122 are fitted onto the corresponding first rotating shafts 1242 and are rotatable around the first rotating shafts 1242. The first driver shaft 13 is provided on the side of the first holder 1241 opposite to the first sun gear 121, and is provided so as to be coaxial with the first sun gear 121. One end of the first driver shaft 13 is connected to the first holder 1241 of the first planetary carrier 124.

[0026] The second planetary gear mechanism 22 is configured as a planetary gear mechanism. The second planetary gear mechanism 22 includes a second sun gear 221, a second planetary gear 222, a second inner ring gear 223, and a second planet carrier 224. The second inner ring gear 223 is fixed and cannot move. The second sun gear 221 is disposed within the second inner ring gear 223 and is coaxial with the second inner ring gear 223. The main shaft of the second motor 21 is coaxial with the second sun gear 221, and the second sun gear 221 is fitted onto the main shaft of the second motor 21. An annular gap exists between the second sun gear 221 and the second inner ring gear 223. The second planetary gear 222 is disposed within the annular gap between the second sun gear 221 and the second inner ring gear 223. The axis of the second planetary gear 222 is parallel to the axis of the second sun gear 221. The second sun gear 221 and the second inner ring gear 223 both mesh with the second planetary gears 222. A plurality of second planetary gears 222, for example, three, may be provided, and the plurality of second planetary gears 222 are evenly distributed in the circumferential direction of the second sun gear 221. The second planet carrier 224 includes a second holder 2241 and a second rotating shaft 2242. The second holder 2241 is provided on the side of the second sun gear 221 opposite to the second motor 21. The second rotating shaft 2242 is parallel to the axis of the second sun gear 221, and one end of the second rotating shaft 2242 is connected to the second holder 2241. The number of second rotation shafts 2242 is the same as the number of second planetary gears 222, and the second rotation shafts 2242 are provided in one-to-one correspondence with the second planetary gears 222, and the second planetary gears 222 are fitted onto the corresponding second rotation shafts 2242 and are rotatable around the second rotation shafts 2242. The second driver shaft 23 is provided on the side of the second holder 2241 opposite to the second sun gear 221, and is provided so as to be coaxial with the second sun gear 221. One end of the second driver shaft 23 is connected to the second holder 2241 of the second planetary carrier 224.

[0027] In this embodiment, the first planetary gear mechanism 12 and the second planetary gear mechanism 22 are both single-row planetary gear mechanisms, and the structure as a speed reducer is compact and highly reliable.

[0028] The first sun gear 121 and the second sun gear 221 are arranged symmetrically, the first planetary gear 122 and the second planetary gear 222 are arranged symmetrically, the first inner ring gear 123 and the second inner ring gear 223 are arranged symmetrically, and the first planetary carrier 124 and the second planetary carrier 224 are arranged symmetrically.

[0029] The gears of the first planetary gear mechanism 12 and the gears of the second planetary gear mechanism 22 are arranged symmetrically, thereby balancing the forces acting on opposite sides of the vehicle. Meanwhile, the first motor 11 and the second motor 21 are connected to the first inner ring gear 123 of the first planetary gear mechanism 12 and the second sun gear of the second planetary gear mechanism 22, respectively, and power is input to the first planetary gear mechanism 12 and the second planetary gear mechanism 22 from the first inner ring gear 123 of the first planetary gear mechanism 12 and the second sun gear of the second planetary gear mechanism 22, respectively, thereby reducing harmonic noise when the first planetary gear mechanism 12 and the second planetary gear mechanism 22 operate simultaneously, improving the NVH performance of the vehicle.

[0030] Example 2 As shown in Figure 2, Figure 2 shows the structure of a dual motor electric drive assembly 100a in Example 2. The dual motor electric drive assembly 100a is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a pure electric vehicle.

[0031] The dual motor electric drive assembly 100a includes a first drive mechanism 1a and a second drive mechanism 2a. The first drive mechanism 1a and the second drive mechanism 2a may be mounted on the same transaxle. The first drive mechanism 1a includes a first motor 11a, a first planetary gear mechanism 12a, and a first driver shaft 13a. The first planetary gear mechanism 12a is mounted between the first driver shaft 13a and the first motor 11a. A main shaft of the first motor 11a is connected to the first planetary gear mechanism 12a, which is connected to the first driver shaft 13a. The first planetary gear mechanism 12a may be a reducer, which can increase the torque output by the first motor 11a by reducing the speed before transmitting it to the first driver shaft 13a to rotate the first driver shaft 13a.

[0032] The second drive mechanism 2a includes a second motor 21a, a second planetary gear mechanism 22a, and a second driver shaft 23a. The second planetary gear mechanism 22a is disposed between the second driver shaft 23a and the second motor 21a. The main shaft of the second motor 21a is connected to the second planetary gear mechanism 22a, and the first planetary gear mechanism 12a is connected to the second driver shaft 23a. The second planetary gear mechanism 22a may be a reducer, and the second planetary gear mechanism 22a can increase the torque output by the second motor 21a by reducing the speed before transmitting it to the second driver shaft 23a to rotate the second driver shaft 23a. The first motor 11a and the second motor 21a are provided between the first planetary gear mechanism 12a and the second planetary gear mechanism 22a, the first driver shaft 13a is provided on the side of the first planetary gear mechanism 12a opposite to the second planetary gear mechanism 22a, and the second driver shaft 23a is provided on the side of the second planetary gear mechanism 22a opposite to the first planetary gear mechanism 12a. The first driver shaft 13a, the second driver shaft 23a, the main shaft of the first motor 11a, and the main shaft of the second motor 21a are provided coaxially.

[0033] In this embodiment, the first planetary gear mechanism 12a is configured as a vertical double-row planetary gear mechanism. The first planetary gear mechanism 12a includes a first sun gear 121a, a first planetary gear 122a, a second planetary gear 125a, a first inner ring gear 123a, a first planet carrier 124a, and a sun gear rotation shaft 120a. The first inner ring gear 123a is arranged coaxially with the main shaft of the first motor 11a. The first inner ring gear 123a includes a connecting member 1232a and a ring gear main body 1231a. The connecting member 1232a is arranged at an end of the ring gear main body 1231a closer to the first motor 11a. The connecting member 1232a connects the ring gear main body 1231a to the main shaft of the first motor 11a. The sun gear rotation shaft 120a is provided within the first inner ring gear 123a and is coaxial with the first inner ring gear 123a. The first sun gear 121a is provided within the first inner ring gear 123a and is coaxial with the first inner ring gear 123a, and is fixedly fitted to the sun gear rotation shaft 120a. The first sun gear 121a cannot rotate around the sun gear rotation shaft 120a. An annular gap exists between the first sun gear 121a and the first inner ring gear 123a. The first planetary gear 122a and the second planetary gear 125a are both provided within the annular gap between the first sun gear 121a and the first inner ring gear 123a. The axes of the first planetary gear 122a and the second planetary gear 125a are both parallel to the axis of the first sun gear 121a. A plurality of first planetary gears 122a, for example, three, may be provided, and the plurality of first planetary gears 122a are evenly distributed in the circumferential direction of the first sun gear 121a. The plurality of first planetary gears 122a mesh with the first sun gear 121a. The number of second planetary gears 125a is the same as the number of first planetary gears 122a. The first planetary gears 122a are provided in one-to-one correspondence with the second planetary gears 125a. The second planetary gears 125a mesh with the corresponding first planetary gears 122a and also mesh with the first inner ring gear 123a.

[0034] The first planetary carrier 124a includes a first holder 1241a, a first rotating shaft 1242a, and a second rotating shaft 1243a. The first holder 1241a is provided on the side of the first sun gear 121a opposite the first motor 11a. The first rotating shaft 1242a and the second rotating shaft 1243a are both parallel to the axis of the first sun gear 121a, and one end of each of the first rotating shaft 1242a and the second rotating shaft 1243a is connected to the first holder 1241a. The number of first rotating shafts 1242a is the same as the number of first planetary gears 122a, and the first rotating shafts 1242a are provided in one-to-one correspondence with the first planetary gears 122a. The first planetary gears 122a are fitted onto the corresponding first rotating shafts 1242a and are rotatable about the first rotating shafts 1242a. The number of second rotating shafts 1243a is the same as the number of second planetary gears 125a, and the second rotating shafts 1243a are provided in one-to-one correspondence with the second planetary gears 125a. The second planetary gears 125a are fitted onto the corresponding second rotating shafts 1243a and are rotatable about the second rotating shafts 1243a. The first driver shaft 13a is provided on the side of the first holder 1241a opposite to the first sun gear 121a and is coaxial with the first sun gear 121a. One end of the first driver shaft 13a is connected to the first holder 1241a of the first planetary carrier 124a.

[0035] The torque output from the main shaft of the first motor 11a is transmitted to the first driver shaft 13a via the first sun gear 121a, the first planetary gear 122a, the second planetary gear 125a, the first inner ring gear 123a, and the first planetary carrier 124a in that order, thereby driving the first driver shaft 13a to rotate.

[0036] In this embodiment, the second planetary gear mechanism 22a is configured as a vertical double-row planetary gear mechanism. The second planetary gear mechanism 22a includes a second sun gear 221a, a third planetary gear 222a, a fourth planetary gear 225a, a second inner ring gear 223a, and a second planet carrier 224a. The second inner ring gear 223a is fixed and cannot move. The second sun gear 221a is disposed within the second inner ring gear 223a and is coaxial with the second inner ring gear 223a. The main shaft of the second motor 21a is coaxial with the second sun gear 221a, and the second sun gear 221a is fitted onto the main shaft of the second motor 21a. An annular gap exists between the second sun gear 221a and the second inner ring gear 223a. The third planetary gear 222a and the fourth planetary gear 225a are both disposed in the annular gap between the second sun gear 221a and the second inner ring gear 223a. The axes of the third planetary gear 222a and the fourth planetary gear 225a are both parallel to the axis of the second sun gear 221a. A plurality of third planetary gears 222a, for example, three, may be provided, and the plurality of third planetary gears 222a are evenly distributed in the circumferential direction of the second sun gear 221a. The plurality of third planetary gears 222a mesh with the second sun gear 221a. The number of fourth planetary gears 225a is the same as the number of third planetary gears 222a. The third planetary gears 222a are disposed in one-to-one correspondence with the fourth planetary gears 225a. The third planetary gears 222a mesh with the corresponding fourth planetary gears 225a and also mesh with the second inner ring gear 223a.

[0037] The second planetary carrier 224a includes a second holder 2241a, a third rotation shaft 2242a, and a fourth rotation shaft 2243a. The second holder 2241a is provided on the side of the second sun gear 221a opposite the second motor 21a. The third rotation shaft 2242a and the fourth rotation shaft 2243a are both parallel to the axis of the second sun gear 221a, and one end of each of the third rotation shaft 2242a and the fourth rotation shaft 2243a is connected to the first holder 1241a. The number of third rotation shafts 2242a is the same as the number of third planetary gears 222a, and the third rotation shafts 2242a are provided in one-to-one correspondence with the third planetary gears 222a. The third planetary gears 222a are fitted onto the corresponding third rotation shafts 2242a and are rotatable about the third rotation shafts 2242a. The number of fourth rotation shafts 2243a is the same as the number of fourth planetary gears 225a, and the fourth rotation shafts 2243a are provided in one-to-one correspondence with the fourth planetary gears 225a. The fourth planetary gears 225a are fitted onto the corresponding fourth rotation shafts 2243a and can rotate around the fourth rotation shafts 2243a. The second driver shaft 23a is provided on the side of the second holder 2241a opposite the second sun gear 221a and is provided coaxially with the second sun gear 221a. One end of the second driver shaft 23a is connected to the second holder 2241a of the second planetary carrier 224a.

[0038] The torque output from the main shaft of the second motor 21a is transmitted to the second driver shaft 23a via the second sun gear 221a, the third planetary gear 222a, the fourth planetary gear 225a, the second inner ring gear 223a, and the second planetary carrier 224a in that order, thereby driving the second driver shaft 23a to rotate.

[0039] In this embodiment, the first planetary gear mechanism 12a and the second planetary gear mechanism 22a are both vertical double-row planetary gear mechanisms, which have a larger transmission ratio than a single-row planetary gear mechanism.

[0040] The first sun gear 121a and the second sun gear 221a are arranged symmetrically, the first planetary gear 122a and the third planetary gear 222a are arranged symmetrically, the second planetary gear 125a and the fourth planetary gear 225a are arranged symmetrically, the first inner ring gear 123a and the second inner ring gear 223a are arranged symmetrically, and the first planetary carrier 124a and the second planetary carrier 224a are arranged symmetrically.

[0041] The gears of the first planetary gear mechanism 12a and the gears of the second planetary gear mechanism 22a are arranged symmetrically, thereby balancing the forces acting on opposite sides of the vehicle. Meanwhile, the first motor 11a and the second motor 21a are connected to the first inner ring gear 123a of the first planetary gear mechanism 12a and the second sun gear 221a of the second planetary gear mechanism 22a, respectively, and power is input from the first inner ring gear 123a and the second sun gear 221a to the first planetary gear mechanism 12a and the second planetary gear mechanism 22a, respectively. This achieves order separation of the first planetary gear mechanism 12a and the second planetary gear mechanism 22a, and further prevents overlapping of the orders of the first planetary gear mechanism 12a and the second planetary gear mechanism 22a. This significantly reduces order noise when the first planetary gear mechanism 12a and the second planetary gear mechanism 22a operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride. Additionally, the first motor 11a and the second motor 21a can be low-power motors. When the first motor 11a and the second motor 21a operate simultaneously, the dual-motor electric drive assembly 100a can output high power, meeting the high-power requirements of automobiles. Because the first motor 11a and the second motor 21a can be controlled independently, the power output of one or both motors can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control of the automobile, resulting in more accurate control. For example, by controlling the rotation speed and torque of the first motor 11a and the second motor 21a, respectively, differential speed and torque distribution between the wheels can be achieved, allowing the automobile to travel in a straight line.

[0042] In one exemplary embodiment, the first driver shaft 13, the first planetary gear mechanism 12, the first motor 11, the second motor 21, the second planetary gear mechanism 22, and the second driver shaft 23 are arranged in sequence and coaxially.

[0043] When arranged in this manner, the dual motor electric drive assembly can extend along the transaxle and has small radial dimensions, a compact structure, and a small space footprint.

[0044] Example 3 As shown in Figure 3, the structure of a dual motor electric drive assembly 100b in Example 3 is shown. The dual motor electric drive assembly 100b is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a pure electric vehicle.

[0045] The dual motor electric drive assembly 100b includes a first drive mechanism 1b and a second drive mechanism 2b. The first drive mechanism 1b and the second drive mechanism 2b may be mounted on the same transaxle. The first drive mechanism 1b includes a first motor 11b, a first planetary gear mechanism 12b, and a first driver shaft 13b. The first planetary gear mechanism 12b is mounted between the first driver shaft 13b and the first motor 11b. A main shaft of the first motor 11b is connected to the first planetary gear mechanism 12b, which is connected to the first driver shaft 13b. The first planetary gear mechanism 12b may be a reducer, which can increase the torque output by the first motor 11b by reducing the speed before transmitting it to the first driver shaft 13b to rotate the first driver shaft 13b.

[0046] The second drive mechanism 2b includes a second motor 21b, a second planetary gear mechanism 22b, and a second driver shaft 23b. The second planetary gear mechanism 22b is disposed between the second driver shaft 23b and the second motor 21b. The main shaft of the second motor 21b is connected to the second planetary gear mechanism 22b, and the first planetary gear mechanism 12b is connected to the second driver shaft 23b. The second planetary gear mechanism 22b may be a reducer, and the second planetary gear mechanism 22b can increase the torque output by the second motor 21b by reducing the speed before transmitting it to the second driver shaft 23b to rotate the second driver shaft 23b. The first motor 11b and the second motor 21b are provided between the first planetary gear mechanism 12b and the second planetary gear mechanism 22b, the first driver shaft 13b is provided on the side of the first planetary gear mechanism 12b opposite the second planetary gear mechanism 22b, and the second driver shaft 23b is provided on the side of the second planetary gear mechanism 22b opposite the first planetary gear mechanism 12b. The first driver shaft 13b, the second driver shaft 23b, the main shaft of the first motor 11b, and the main shaft of the second motor 21b are provided coaxially.

[0047] In this embodiment, the first planetary gear mechanism 12b is configured as a horizontal double-row planetary gear mechanism. The first planetary gear mechanism 12b includes a first sun gear 121b, a first planetary gear 122b, a second planetary gear 125b, a first inner ring gear 123b, and a first planet carrier 124b. The first inner ring gear 123b is fixed and cannot move. The first sun gear 121b is located on the opposite side of the first inner ring gear 123b from the first motor 11b, coaxial with the first inner ring gear 123b, and the outer diameter of the first sun gear 121b is smaller than the inner diameter of the first inner ring gear 123b. The main shaft of the first motor 11b is coaxial with the first sun gear 121b, and the first sun gear 121b is fitted onto the main shaft of the first motor 11b.

[0048] The axes of the first planetary gear 122b and the second planetary gear 125b are both parallel to the axis of the first sun gear 121b. A plurality of first planetary gears 122b, for example, three, may be provided, and the plurality of first planetary gears 122b are evenly distributed in the circumferential direction of the first sun gear 121b. The plurality of first planetary gears 122b mesh with the first sun gear 121b. The number of second planetary gears 125b is the same as the number of first planetary gears 122b. The second planetary gears 125b are provided within the first inner ring gear 123b. The first planetary gears 122b are provided in one-to-one correspondence with the second planetary gears 125b. The second planetary gears 125b are provided coaxially with the corresponding first planetary gears 122b and mesh with the first inner ring gear 123b. The outer diameter of the first planetary gear 122b is larger than the outer diameter of the second planetary gear 125b.

[0049] The first planetary carrier 124b includes a first holder 1241b and a first rotation shaft 1242b. The first holder 1241b is provided on the side of the first planetary gear 122b opposite to the second planetary gear 125b. The first rotation shaft 1242b is parallel to the axis of the first sun gear 121b, and one end of the first rotation shaft 1242b is connected to the first holder 1241b. The number of first rotating shafts 1242b is the same as the number of first planetary gears 122b, the first rotating shafts 1242b are provided in one-to-one correspondence with the first planetary gears 122b, the first rotating shafts 1242b are provided in one-to-one correspondence with the second planetary gears 125b, the first planetary gears 122b are fitted onto the corresponding first rotating shafts 1242b and are rotatable about the first rotating shafts 1242b, and the second planetary gears 125b are fitted onto the corresponding first rotating shafts 1242b and are rotatable about the first rotating shafts 1242b. The first driver shaft 13b is provided on the side of the first holder 1241b opposite to the first sun gear 121b and is provided so as to be coaxial with the first sun gear 121b. One end of the first driver shaft 13b is connected to the first holder 1241b of the first planetary carrier 124b.

[0050] The torque output from the main shaft of the first motor 11b is sent to the first driver shaft 13b via the first planetary gear mechanism 12b, thereby driving the first driver shaft 13b to rotate.

[0051] In this embodiment, the second planetary gear mechanism 22b is configured as a horizontal double-row planetary gear mechanism. The second planetary gear mechanism 22b includes a second sun gear 221b, a third planetary gear 222b, a fourth planetary gear 225b, a second inner ring gear 223b, a second planet carrier 224b, and a sun gear rotation shaft 220b. The second inner ring gear 223b is provided coaxially with the main shaft of the second motor 21b. The second inner ring gear 223b includes a connecting member 2232b and a ring gear main body 2231b. The connecting member 2232b is provided at one end of the ring gear main body 2231b. The connecting member 2232b is connected to the ring gear main body 2231b and the main shaft of the second motor 21b, respectively. The connecting member 2232b may be provided at one end of the ring gear main body 2231b. The sun gear rotation shaft 220b is provided on the opposite side of the second inner ring gear 223b from the second motor 21b, and is coaxial with the second inner ring gear 223b, and the sun gear rotation shaft 220b is fixedly provided. The second sun gear 221b is fixedly fitted onto the sun gear rotation shaft 220b, and the second sun gear 221b cannot rotate around the sun gear rotation shaft 220b. In this way, the second sun gear 221b is provided on the opposite side of the second inner ring gear 223b from the second motor 21b, and is coaxial with the second inner ring gear 223b, and the outer diameter of the second sun gear 221b is smaller than the inner diameter of the second inner ring gear 223b.

[0052] The axes of the third planetary gear 222b and the fourth planetary gear 225b are both parallel to the axis of the second sun gear 221b. A plurality of third planetary gears 222b, for example three, may be provided, and the plurality of third planetary gears 222b are evenly distributed in the circumferential direction of the second sun gear 221b. All of the plurality of third planetary gears 222b mesh with the second sun gear 221b. The fourth planetary gears 225b are provided inside the second inner ring gear 223b. The number of fourth planetary gears 225b is the same as the number of third planetary gears 222b. The third planetary gears 222b are provided in one-to-one correspondence with the fourth planetary gears 225b. All of the fourth planetary gears 225b are provided within the second inner ring gear 223b. The fourth planetary gear 225b is provided coaxially with the corresponding third planetary gear 222b and meshes with the second inner ring gear 223b. The outer diameter of the third planetary gear 222b is larger than the outer diameter of the fourth planetary gear 225b.

[0053] The second planetary carrier 224b includes a second holder 2241b and a second rotation shaft 2242b. The second holder 2241b is provided on the opposite side of the third planetary gear 222b from the fourth planetary gear 225b. The second rotation shaft 2242b is parallel to the axis of the second sun gear 221b, and one end of the second rotation shaft 2242b is connected to the second holder 2241b. The number of second rotation shafts 2242b is the same as the number of third planetary gears 222b, the second rotation shafts 2242b are provided in one-to-one correspondence with the third planetary gears 222b, the second rotation shafts 2242b are provided in one-to-one correspondence with the fourth planetary gears 225b, the third planetary gears 222b are fitted onto the corresponding second rotation shafts 2242b and are rotatable about the second rotation shafts 2242b, and the fourth planetary gears 225b are fitted onto the corresponding second rotation shafts 2242b and are rotatable about the second rotation shafts 2242b. The second driver shaft 23b is provided on the side of the second holder 2241b opposite to the second sun gear 221b and is arranged so as to be coaxial with the second sun gear 221b. One end of the second driver shaft 23b is connected to the second holder 2241b of the second planetary carrier 224b.

[0054] The torque output from the main shaft of the second motor 21b is sent to the second driver shaft 23b via the second planetary gear mechanism 22b, thereby driving the second driver shaft 23b to rotate.

[0055] Since the first planetary gear mechanism 12b and the second planetary gear mechanism 22b are both horizontal double-row planetary gear mechanisms, the transmission ratios of the first planetary gear mechanism 12b and the second planetary gear mechanism 22b are both greater than the transmission ratio of a single-row planetary gear mechanism. Furthermore, the radial dimension of the horizontal double-row planetary gear mechanism is smaller than that of a vertical double-row planetary gear mechanism.

[0056] The first sun gear 121b and the second sun gear 221b are arranged symmetrically, the first planetary gear 122b and the third planetary gear 222b are arranged symmetrically, the second planetary gear 125b and the fourth planetary gear 225b are arranged symmetrically, the first inner ring gear 123b and the second inner ring gear 223b are arranged symmetrically, and the first planetary carrier 124b and the second planetary carrier 224b are arranged symmetrically.

[0057] The gears of the first planetary gear mechanism 12b and the gears of the second planetary gear mechanism 22b are arranged symmetrically, thereby balancing the forces acting on opposite sides of the vehicle. Meanwhile, the first motor 11b and the second motor 21b are connected to the first sun gear 121b of the first planetary gear mechanism 12b and the second inner ring gear 223b of the second planetary gear mechanism 22b, respectively, and power is input from the first sun gear 121b and the second inner ring gear 223b to the first planetary gear mechanism 12b and the second planetary gear mechanism 22b, respectively, thereby realizing order separation of the first planetary gear mechanism 12b and the second planetary gear mechanism 22b and further preventing overlapping of the orders of the first planetary gear mechanism 12b and the second planetary gear mechanism 22b. This significantly reduces order noise when the first planetary gear mechanism 12b and the second planetary gear mechanism 22b operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride. Additionally, the first motor 11b and the second motor 21b can be low-power motors. When the first motor 11b and the second motor 21b operate simultaneously, the dual-motor electric drive assembly 100b can output high power, meeting the high-power requirements of automobiles. Because the first motor 11b and the second motor 21b can be controlled independently, the power output of one or both motors can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control for automobiles, resulting in more precise control. For example, by controlling the rotation speed and torque of the first motor 11b and the second motor 21b, differential speed and torque distribution between the wheels can be achieved, enabling the automobile to travel in a straight line.

[0058] Example 4 As shown in Figure 4, the structure of a dual motor electric drive assembly 100c in Example 4 is shown. The dual motor electric drive assembly 100c is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a pure electric vehicle.

[0059] The dual motor electric drive assembly 100c includes a first drive mechanism 1c and a second drive mechanism 2c. The first drive mechanism 1c and the second drive mechanism 2c may be mounted on the same transaxle. The first drive mechanism 1c includes a first motor 11c, a first planetary gear mechanism 12c, and a first driver shaft 13c. The first planetary gear mechanism 12c is mounted between the first driver shaft 13c and the first motor 11c. A main shaft of the first motor 11c is connected to the first planetary gear mechanism 12c, which is connected to the first driver shaft 13c. The first planetary gear mechanism 12c may be a reducer, which can increase the torque output by the first motor 11c by reducing the speed before transmitting it to the first driver shaft 13c to rotate the first driver shaft 13c.

[0060] The second drive mechanism 2c includes a second motor 21c, a second planetary gear mechanism 22c, and a second driver shaft 23c. The second planetary gear mechanism 22c is disposed between the second driver shaft 23c and the second motor 21c. A main shaft of the second motor 21c is connected to the second planetary gear mechanism 22c, and the first planetary gear mechanism 12c is connected to the second driver shaft 23c. The second planetary gear mechanism 22c may be a reducer, and the second planetary gear mechanism 22c can increase the torque output by the second motor 21c by reducing the speed before transmitting it to the second driver shaft 23c to rotate the second driver shaft 23c. The first motor 11c and the second motor 21c are provided between the first planetary gear mechanism 12c and the second planetary gear mechanism 22c, the first driver shaft 13c is provided on the side of the first planetary gear mechanism 12c opposite to the second planetary gear mechanism 22c, and the second driver shaft 23c is provided on the side of the second planetary gear mechanism 22c opposite to the first planetary gear mechanism 12c. The first driver shaft 13c, the second driver shaft 23c, the main shaft of the first motor 11c, and the main shaft of the second motor 21c are provided coaxially.

[0061] In this embodiment, the first planetary gear mechanism 12c is configured as a horizontal double-row planetary gear mechanism. The first planetary gear mechanism 12c includes a first sun gear 121c, a second sun gear 123c, a first planetary gear 122c, a second planetary gear 125c, a first planetary carrier 124c, and a sun gear rotation shaft 120c. The first sun gear 121c is fitted onto the main shaft of the first motor 11c. The second sun gear 123c is provided on the opposite side of the first sun gear 121c to the first motor 11c. The second sun gear 123c is provided coaxially with the first sun gear 121c. The sun gear rotation shaft 120c is provided on the opposite side of the first sun gear 121c to the first motor 11c, and the sun gear rotation shaft 120c is provided coaxially with the first sun gear 121c. The second sun gear 123c is fixedly fitted onto the sun gear rotation shaft 120c. The second sun gear 123c cannot rotate around the sun gear rotation shaft 120c. The outer diameter of the second sun gear 123c may be larger than the outer diameter of the first sun gear 121c.

[0062] The axes of the first planetary gear 122c and the second planetary gear 125c are both parallel to the axis of the first sun gear 121c. A plurality of first planetary gears 122c, for example, three, may be provided, and the plurality of first planetary gears 122c are evenly distributed in the circumferential direction of the first sun gear 121c. The plurality of first planetary gears 122c mesh with the first sun gear 121c. The number of second planetary gears 125c is the same as the number of first planetary gears 122c. The plurality of second planetary gears 125c are evenly distributed in the circumferential direction of the second sun gear 123c. The first planetary gears 122c are provided in one-to-one correspondence with the second planetary gears 125c. The second planetary gears 125c are provided coaxially with their corresponding first planetary gears 122c and mesh with the second sun gears 123c. The outer diameter of the first planetary gear 122c is larger than the outer diameter of the second planetary gear 125c.

[0063] The first planetary carrier 124c includes a first holder 1241c and a first rotation shaft 1242c. The first holder 1241c is provided on the opposite side of the second planetary gear 125c to the first planetary gear 122c. The first rotation shaft 1242c is parallel to the axis of the first sun gear 121c, and one end of the first rotation shaft 1242c is connected to the first holder 1241c. The number of first rotating shafts 1242c is the same as the number of first planetary gears 122c, the first rotating shafts 1242c are provided in one-to-one correspondence with the first planetary gears 122c, the first rotating shafts 1242c are provided in one-to-one correspondence with the second planetary gears 125c, the first planetary gears 122c are fitted onto the corresponding first rotating shafts 1242c and are rotatable about the first rotating shafts 1242c, and the second planetary gears 125c are fitted onto the corresponding first rotating shafts 1242c and are rotatable about the first rotating shafts 1242c. The first driver shaft 13c is provided on the side of the first holder 1241c opposite to the second sun gear 123c and is provided so as to be coaxial with the second sun gear 123c. One end of the first driver shaft 13c is connected to a first holder 1241c of the first planetary carrier 124c.

[0064] The torque output from the main shaft of the first motor 11c is sent to the first driver shaft 13c via the first planetary gear mechanism 12c, thereby driving the first driver shaft 13c to rotate.

[0065] In this embodiment, the second planetary gear mechanism 22c is configured as a horizontal double-row planetary gear mechanism. The second planetary gear mechanism 22c includes a third sun gear 221c, a fourth sun gear 223c, a third planetary gear 222c, a fourth planetary gear 225c, and a second planetary carrier 224c. The third sun gear 221c is fixedly mounted. A through hole 2210c is provided in the third sun gear 221c, and passes through the third sun gear 221c along the axial direction of the third sun gear 221c. The through hole 2210c is provided in the central portion of the third sun gear 221c. The main shaft of the second motor 21c is provided coaxially with the third sun gear 221c and is inserted through the through hole 2210c of the third sun gear 221c. The third sun gear 221c is loosely fitted onto the main shaft of the second motor 21c. The fourth sun gear 223c is provided on the opposite side of the third sun gear 221c from the second motor 21c. The fourth sun gear 223c is provided coaxially with the third sun gear 221c. The fourth sun gear 223c is fitted onto the main shaft of the second motor 21c and fixedly connected to the main shaft of the second motor 21c. The outer diameter of the fourth sun gear 223c may be larger than the outer diameter of the third sun gear 221c.

[0066] The axes of the third planetary gear 222c and the fourth planetary gear 225c are both parallel to the axis of the third sun gear 221c. A plurality of third planetary gears 222c, for example, three, may be provided, and the plurality of third planetary gears 222c are evenly distributed in the circumferential direction of the third sun gear 221c. All of the plurality of third planetary gears 222c mesh with the third sun gear 221c. The number of fourth planetary gears 225c is the same as the number of third planetary gears 222c. The plurality of fourth planetary gears 225c are evenly distributed in the circumferential direction of the fourth sun gear 223c. The third planetary gears 222c are provided in one-to-one correspondence with the fourth planetary gears 225c. The fourth planetary gears 225c are provided coaxially with the corresponding third planetary gears 222c and mesh with the fourth sun gear 223c. The outer diameter of the third planetary gear 222c is larger than the outer diameter of the fourth planetary gear 225c.

[0067] The second planetary carrier 224c includes a second holder 2241c and a second rotation shaft 2242c. The second holder 2241c is provided on the opposite side of the fourth planetary gear 225c from the third planetary gear 222c. The second rotation shaft 2242c is parallel to the axis of the third sun gear 221c, and one end of the second rotation shaft 2242c is connected to the second holder 2241c. The number of second rotation shafts 2242c is the same as the number of third planetary gears 222c, the second rotation shafts 2242c are provided in one-to-one correspondence with the third planetary gears 222c, the second rotation shafts 2242c are provided in one-to-one correspondence with the fourth planetary gears 225c, the third planetary gears 222c are fitted onto the corresponding second rotation shafts 2242c and are rotatable about the second rotation shafts 2242c, and the fourth planetary gears 225c are fitted onto the corresponding second rotation shafts 2242c and are rotatable about the second rotation shafts 2242c. The second driver shaft 23c is provided on the side of the second holder 2241c opposite to the second sun gear 123c and is arranged coaxially with the third sun gear 221c. One end of the second driver shaft 23c is connected to the second holder 2241c of the second planetary carrier 224c.

[0068] The torque output from the main shaft of the second motor 21c is sent to the second driver shaft 23c via the second planetary gear mechanism 22c, thereby driving the second driver shaft 23c to rotate.

[0069] The first planetary gear mechanism 12c and the second planetary gear mechanism 22c are both horizontal double-row planetary gear mechanisms, and therefore the transmission ratios of the first planetary gear mechanism 12c and the second planetary gear mechanism 22c are both greater than the transmission ratio of a single-row planetary gear mechanism. Furthermore, the first planetary gear mechanism 12c and the second planetary gear mechanism 22c in this embodiment do not have inner ring gears, but instead use second sun gears 123c and fourth sun gears 223c, resulting in a more compact structure and lower manufacturing costs.

[0070] The first sun gear 121c and the third sun gear 221c are arranged symmetrically, the second sun gear 123c and the fourth sun gear 223c are arranged symmetrically, the first planetary gear 122c and the third planetary gear 222c are arranged symmetrically, the second planetary gear 125c and the fourth planetary gear 225c are arranged symmetrically, and the first planetary carrier 124c and the second planetary carrier 224c are arranged symmetrically.

[0071] The gears of the first planetary gear mechanism 12c and the gears of the second planetary gear mechanism 22c are arranged symmetrically, thereby balancing the forces acting on opposite sides of the vehicle. Meanwhile, the first motor 11c and the second motor 21c are connected to the first sun gear 121c of the first planetary gear mechanism 12c and the fourth sun gear 223c of the second planetary gear mechanism 22c, respectively, and power is input from the first sun gear 121c and the fourth sun gear 223c to the first planetary gear mechanism 12c and the second planetary gear mechanism 22c, respectively. This achieves order separation of the first planetary gear mechanism 12c and the second planetary gear mechanism 22c and prevents overlapping of the orders of the first planetary gear mechanism 12c and the second planetary gear mechanism 22c. This significantly reduces order noise when the first planetary gear mechanism 12c and the second planetary gear mechanism 22c operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride. Additionally, the first motor 11c and the second motor 21c can be low-power motors. When the first motor 11c and the second motor 21c operate simultaneously, the dual-motor electric drive assembly 100c can output high power, meeting the high-power requirements of automobiles. Because the first motor 11c and the second motor 21c can be controlled independently, the power output of one or both motors can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control of the automobile, resulting in more precise control. For example, by controlling the rotation speed and torque of the first motor 11c and the second motor 21c, differential speed and torque distribution between the wheels can be achieved, allowing the automobile to travel in a straight line.

[0072] Example 5 As shown in Figure 5, the structure of a dual motor electric drive assembly 100d in Example 5 is shown. The dual motor electric drive assembly 100d is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a pure electric vehicle.

[0073] The dual motor electric drive assembly 100d includes a first drive mechanism 1d and a second drive mechanism 2d, which may be mounted on the same transaxle.

[0074] The first drive mechanism 1d includes a first motor 11d, a first gear transmission 12d, and a first driver shaft 13d. The first gear transmission 12d is disposed between the first driver shaft 13d and the first motor 11d. A main shaft of the first motor 11d is connected to the first gear transmission 12d, which is connected to the first driver shaft 13d. The first gear transmission 12d may be a reducer, which can increase the torque output by the first motor 11d by reducing the speed and then transmit it to the first driver shaft 13d to rotate the first driver shaft 13d.

[0075] The second drive mechanism 2d includes a second motor 21d, a second gear transmission 22d, and a second driver shaft 23d. The second gear transmission 22d is disposed between the second driver shaft 23d and the second motor 21d. The main shaft of the second motor 21d is connected to the second gear transmission 22d, and the first gear transmission 12d is connected to the second driver shaft 23d. The second gear transmission 22d may be a reducer, which can increase the torque output by the second motor 21d by reducing the speed and then transmit it to the second driver shaft 23d to rotate the second driver shaft 23d. The first motor 11d and the second motor 21d are provided between the first gear transmission mechanism 12d and the second gear transmission mechanism 22d, the first driver shaft 13d is provided on the side of the first gear transmission mechanism 12d opposite the second gear transmission mechanism 22d, and the second driver shaft 23d is provided on the side of the second gear transmission mechanism 22d opposite the first gear transmission mechanism 12d. The first driver shaft 13d, the second driver shaft 23d, the main shaft of the first motor 11d, and the main shaft of the second motor 21d are provided coaxially.

[0076] The gears of the first gear transmission mechanism 12d and the gears of the second gear transmission mechanism 22d are arranged to be positionally symmetrical, and the positional symmetry is mirror symmetry, i.e., for every gear in the first gear transmission mechanism 12d, there is a positionally symmetrical gear in the second gear transmission mechanism 22d. At least two of the symmetrically arranged gears in the first gear transmission mechanism 12d and the second gear transmission mechanism 22d have different numbers of teeth.

[0077]

[0023] At least two of the first gear transmission 12d and the second gear transmission 22d have different numbers of teeth, and the first gear transmission 12d and the second gear transmission 22d are not completely identical, but the orders of the first gear transmission 12d and the second gear transmission 22d are separated, and overlapping of the orders of the first gear transmission 12d and the second gear transmission 22d is avoided. This significantly reduces order noise when the first gear transmission 12d and the second gear transmission 22d operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride. Furthermore, the first motor 11d and the second motor 21d may be low-power motors. When the first motor 11d and the second motor 21d operate simultaneously, the dual-motor electric drive assembly 100d can output high power, meeting the high-power requirements of the vehicle. Because the first motor 11d and the second motor 21d can be controlled independently, the power output of one or both sides can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control of the vehicle to be realized, resulting in more accurate control. For example, by controlling the rotation speed and torque of the first motor 11d and the second motor 21d, respectively, differential speed and torque distribution between the wheels can be realized, allowing the vehicle to travel in a straight line.

[0078] In one exemplary embodiment, the first gear transmission mechanism 12d is configured as a single-row planetary gear mechanism. The first gear transmission mechanism 12d includes a first sun gear 121d, a first planetary gear 122d, a first inner ring gear 123d, and a first planet carrier 124d. The first inner ring gear 123d is fixed and cannot move. The first sun gear 121d is disposed within the first inner ring gear 123d and is coaxial with the first inner ring gear 123d. The main shaft of the first motor 11d is coaxial with the first sun gear 121d, and the first sun gear 121d is fitted to the main shaft of the first motor 11d. An annular gap exists between the first sun gear 121d and the first inner ring gear 123d. The first planetary gear 122d is disposed within the annular gap between the first sun gear 121d and the first inner ring gear 123d. The axis of the first planetary gear 122d is parallel to the axis of the first sun gear 121d. Both the first sun gear 121d and the first inner ring gear 123d mesh with the first planetary gear 122d. A plurality of first planetary gears 122d, for example, three, may be provided, and the plurality of first planetary gears 122d may be evenly distributed in the circumferential direction of the first sun gear 121d. The first planet carrier 124d includes a first holder 1241d and a first rotating shaft 1242d. The first holder 1241d is provided on the side of the first sun gear 121d opposite the first motor 11d. The first rotating shaft 1242d is parallel to the axis of the first sun gear 121d, and one end of the first rotating shaft 1242d is connected to the first holder 1241d. The number of first rotating shafts 1242d is the same as the number of first planetary gears 122d, and the first rotating shafts 1242d are provided in one-to-one correspondence with the first planetary gears 122d, and the first planetary gears 122d are fitted onto the corresponding first rotating shafts 1242d and can rotate around the first rotating shafts 1242d. The first driver shaft 13d is provided on the side of the first holder 1241d opposite the first sun gear 121d, and is provided so as to be coaxial with the first sun gear 121d. One end of the first driver shaft 13d is connected to the first holder 1241d of the first planetary carrier 124d.

[0079] The torque output from the main shaft of the first motor 11d is transmitted to the first driver shaft 13d via the first sun gear 121d, the first planetary gear 122d, the first inner ring gear 123d, and the first planetary carrier 124d in this order, thereby driving and rotating the first driver shaft 13d. The second driver shaft 23d is circumferentially circumferentially connected to the wheels, thereby driving and rotating the wheels.

[0080] The second gear transmission mechanism 22d is configured as a planetary gear mechanism. The second gear transmission mechanism 22d includes a second sun gear 221d, a second planetary gear 222d, a second inner ring gear 223d, and a second planet carrier 224d. The second inner ring gear 223d is fixed and cannot move. The second sun gear 221d is disposed within the second inner ring gear 223d and is coaxial with the second inner ring gear 223d. The main shaft of the second motor 21d is coaxial with the second sun gear 221d, and the second sun gear 221d is fitted onto the main shaft of the second motor 21d. An annular gap exists between the second sun gear 221d and the second inner ring gear 223d. The second planetary gear 222d is disposed within the annular gap between the second sun gear 221d and the second inner ring gear 223d. The axis of the second planetary gear 222d is parallel to the axis of the second sun gear 221d. Both the second sun gear 221d and the second inner ring gear 223d mesh with the second planetary gear 222d. A plurality of second planetary gears 222d, for example, three, may be provided, and the plurality of second planetary gears 222d may be evenly distributed in the circumferential direction of the second sun gear 221d. The second planet carrier 224d includes a second holder 2241d and a second rotating shaft 2242d. The second holder 2241d is provided on the side of the second sun gear 221d opposite the second motor 21d. The second rotating shaft 2242d is parallel to the axis of the second sun gear 221d, and one end of the second rotating shaft 2242d is connected to the second holder 2241d. The number of second rotation shafts 2242d is the same as the number of second planetary gears 222d, and the second rotation shafts 2242d are provided in one-to-one correspondence with the second planetary gears 222d, and the second planetary gears 222d are fitted onto the corresponding second rotation shafts 2242d and are rotatable around the second rotation shafts 2242d. The second driver shaft 23d is provided on the side of the second holder 2241d opposite the second sun gear 221d, and is provided so as to be coaxial with the second sun gear 221d. One end of the second driver shaft 23d is connected to the second holder 2241d of the second planetary carrier 224d.

[0081] The torque output from the main shaft of second motor 21d is transmitted to second driver shaft 23d via second sun gear 221d, second planetary gear 222d, second inner ring gear 223d, and second planetary carrier 224d in this order, thereby driving and rotating second driver shaft 23d. Second driver shaft 23d is circumferentially circumferentially connected to wheels, thereby driving and rotating the wheels.

[0082] In this embodiment, the first gear transmission mechanism 12d and the second gear transmission mechanism 22d are both single-row planetary gear mechanisms, and the structure as a reducer is compact and highly reliable.

[0083] The first sun gear 121d and the second sun gear 221d are arranged symmetrically, the first planetary gear 122d and the second planetary gear 222d are arranged symmetrically, the first inner ring gear 123d and the second inner ring gear 223d are arranged symmetrically, and the first planetary carrier 124d and the second planetary carrier 224d are arranged symmetrically. At least one of the numbers of teeth of the first sun gear 121d and the second sun gear 221d, the numbers of teeth of the first planetary gears 122d and the second planetary gears 222d, and the numbers of teeth of the first inner ring gear 123d and the second inner ring gear 223d is different, so that the first gear transmission mechanism 12d and the second gear transmission mechanism 22d are not completely symmetrical, thereby reducing harmonic noise when the first gear transmission mechanism 12d and the second gear transmission mechanism 22d operate simultaneously.

[0084] In one exemplary embodiment, the first sun gear 121d and the second sun gear 221d have different numbers of teeth, the first planetary gear 122d and the second planetary gear 222d have different numbers of teeth, and the first inner ring gear 123d and the second inner ring gear 223d have different numbers of teeth.

[0085] In this way, the number of teeth between all symmetrically arranged gears is different, which further reduces the harmonic noise when the first gear transmission mechanism 12d and the second gear transmission mechanism 22d operate simultaneously, improving the NVH performance of the automobile and providing a more comfortable ride.

[0086] Example 6 As shown in Figure 6, a dual motor electric drive assembly 100e according to a sixth embodiment is shown. The dual motor electric drive assembly 100e is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a purely electric vehicle.

[0087] The dual motor electric drive assembly 100e includes a first drive mechanism 1e and a second drive mechanism 2e. The first drive mechanism 1e and the second drive mechanism 2e may be mounted on the same transaxle. The first drive mechanism 1e includes a first motor 11e, a first gear transmission 12e, and a first driver shaft 13e. The first gear transmission 12e is mounted between the first driver shaft 13e and the first motor 11e. A main shaft of the first motor 11e is connected to the first gear transmission 12e, which in turn is connected to the first driver shaft 13e. The first gear transmission 12e may be a reducer, which can increase the torque output by the first motor 11e by reducing the speed before transmitting it to the first driver shaft 13e to rotate the first driver shaft 13e.

[0088] The second drive mechanism 2e includes a second motor 21e, a second gear transmission 22e, and a second driver shaft 23e. The second gear transmission 22e is disposed between the second driver shaft 23e and the second motor 21e. A main shaft of the second motor 21e is connected to the second gear transmission 22e, and the first gear transmission 12e is connected to the second driver shaft 23e. The second gear transmission 22e may be a reducer, which can increase the torque output by the second motor 21e by reducing the speed and then transmit the torque to the second driver shaft 23e to rotate the second driver shaft 23e. The first motor 11e and the second motor 21e are provided between the first gear transmission mechanism 12e and the second gear transmission mechanism 22e, the first driver shaft 13e is provided on the side of the first gear transmission mechanism 12e opposite to the second gear transmission mechanism 22e, and the second driver shaft 23e is provided on the side of the second gear transmission mechanism 22e opposite to the first gear transmission mechanism 12e. The first driver shaft 13e, the second driver shaft 23e, the main shaft of the first motor 11e, and the main shaft of the second motor 21e are provided coaxially.

[0089] In this embodiment, the first gear transmission mechanism 12e is configured as a vertical double-row planetary gear mechanism. The first gear transmission mechanism 12e includes a first sun gear 121e, a first planetary gear 122e, a second planetary gear 125e, a first inner ring gear 123e, and a first planet carrier 124e. The first inner ring gear 123e is fixed and cannot move. The first sun gear 121e is disposed within the first inner ring gear 123e and is coaxial with the first inner ring gear 123e. The main shaft of the first motor 11e is coaxial with the first sun gear 121e, and the first sun gear 121e is fitted onto the main shaft of the first motor 11e. An annular gap exists between the first sun gear 121e and the first inner ring gear 123e. The first planetary gear 122e and the second planetary gear 125e are both disposed in the annular gap between the first sun gear 121e and the first inner ring gear 123e. The axes of the first planetary gear 122e and the second planetary gear 125e are both parallel to the axis of the first sun gear 121e. A plurality of first planetary gears 122e, for example, three, may be provided, and the plurality of first planetary gears 122e are evenly distributed in the circumferential direction of the first sun gear 121e. The plurality of first planetary gears 122e mesh with the first sun gear 121e. The number of second planetary gears 125e is the same as the number of first planetary gears 122e. The first planetary gears 122e are disposed in one-to-one correspondence with the second planetary gears 125e. Second planetary gears 125e mesh with corresponding first planetary gears 122e and also mesh with first inner ring gear 123e.

[0090] The first planetary carrier 124e includes a first holder 1241e, a first rotation shaft 1242e, and a second rotation shaft 1243e. The first holder 1241e is provided on the side of the first sun gear 121e opposite the first motor 11e. The first rotation shaft 1242e and the second rotation shaft 1243e are both parallel to the axis of the first sun gear 121e, and one end of each of the first rotation shaft 1242e and the second rotation shaft 1243e is connected to the first holder 1241e. The number of first rotation shafts 1242e is the same as the number of first planetary gears 122e, and the first rotation shafts 1242e are provided in one-to-one correspondence with the first planetary gears 122e. The first planetary gears 122e are fitted onto the corresponding first rotation shafts 1242e and are rotatable about the first rotation shafts 1242e. The number of second rotation shafts 1243e is the same as the number of second planetary gears 125e, and the second rotation shafts 1243e are provided in one-to-one correspondence with the second planetary gears 125e, and the second planetary gears 125e are fitted onto their corresponding second rotation shafts 1243e and can rotate around the second rotation shafts 1243e. The first driver shaft 13e is provided on the side of the first holder 1241e opposite the first sun gear 121e, and is provided so as to be coaxial with the first sun gear 121e. One end of the first driver shaft 13e is connected to the first holder 1241e of the first planetary carrier 124e.

[0091] The torque output from the main shaft of the first motor 11e is transmitted to the first driver shaft 13e via the first sun gear 121e, the first planetary gear 122e, the second planetary gear 125e, the first inner ring gear 123e, and the first planetary carrier 124e in that order, thereby driving the first driver shaft 13e to rotate.

[0092] In this embodiment, the second gear transmission mechanism 22e is configured as a vertical double-row planetary gear mechanism. The second gear transmission mechanism 22e includes a second sun gear 221e, a third planetary gear 222e, a fourth planetary gear 225e, a second inner ring gear 223e, and a second planet carrier 224e. The second inner ring gear 223e is fixed and cannot move. The second sun gear 221e is disposed within the second inner ring gear 223e and is coaxial with the second inner ring gear 223e. The main shaft of the second motor 21e is coaxial with the second sun gear 221e, and the second sun gear 221e is fitted onto the main shaft of the second motor 21e. An annular gap exists between the second sun gear 221e and the second inner ring gear 223e. The third planetary gear 222e and the fourth planetary gear 225e are both disposed in the annular gap between the second sun gear 221e and the second inner ring gear 223e. The axes of the third planetary gear 222e and the fourth planetary gear 225e are both parallel to the axis of the second sun gear 221e. A plurality of third planetary gears 222e, for example, three, may be provided, and the plurality of third planetary gears 222e are evenly distributed in the circumferential direction of the second sun gear 221e. The plurality of third planetary gears 222e mesh with the second sun gear 221e. The number of fourth planetary gears 225e is the same as the number of third planetary gears 222e. The third planetary gears 222e are disposed in one-to-one correspondence with the fourth planetary gears 225e. The third planetary gears 222e mesh with the corresponding fourth planetary gears 225e and also mesh with the second inner ring gear 223e.

[0093] The second planetary carrier 224e includes a second holder 2241e, a third rotation shaft 2242e, and a fourth rotation shaft 2243e. The second holder 2241e is provided on the side of the second sun gear 221e opposite the second motor 21e. The third rotation shaft 2242e and the fourth rotation shaft 2243e are both parallel to the axis of the second sun gear 221e, and one end of each of the third rotation shaft 2242e and the fourth rotation shaft 2243e is connected to the first holder 1241e. The number of third rotation shafts 2242e is the same as the number of third planetary gears 222e, and the third rotation shafts 2242e are provided in one-to-one correspondence with the third planetary gears 222e. The third planetary gears 222e are fitted onto the corresponding third rotation shafts 2242e and are rotatable about the third rotation shafts 2242e. The number of fourth rotation shafts 2243e is the same as the number of fourth planetary gears 225e, and the fourth rotation shafts 2243e are provided in one-to-one correspondence with the fourth planetary gears 225e. The fourth planetary gears 225e are fitted onto the corresponding fourth rotation shafts 2243e and can rotate around the fourth rotation shafts 2243e. The second driver shaft 23e is provided on the side of the second holder 2241e opposite the second sun gear 221e and is coaxial with the second sun gear 221e. One end of the second driver shaft 23e is connected to the second holder 2241e of the second planetary carrier 224e.

[0094] The torque output from the main shaft of the second motor 21e is transmitted to the second driver shaft 23e via the second sun gear 221e, the third planetary gear 222e, the fourth planetary gear 225e, the second inner ring gear 223e, and the second planetary carrier 224e in that order, thereby driving the second driver shaft 23e to rotate.

[0095] In this embodiment, the first gear transmission mechanism 12e and the second gear transmission mechanism 22e are both vertical double-row planetary gear mechanisms, which have a larger transmission ratio than a single-row planetary gear mechanism.

[0096] The first sun gear 121e and the second sun gear 221e are arranged symmetrically, the first planetary gear 122e and the third planetary gear 222e are arranged symmetrically, the second planetary gear 125e and the fourth planetary gear 225e are arranged symmetrically, the first inner ring gear 123e and the second inner ring gear 223e are arranged symmetrically, and the first planetary carrier 124e and the second planetary carrier 224e are arranged symmetrically. At least one of the numbers of teeth of the first sun gear 121e and the second sun gear 221e, the numbers of teeth of the first planetary gear 122e and the third planetary gear 222e, the numbers of teeth of the second planetary gears 125e and the fourth planetary gears 225e, and the numbers of teeth of the first inner ring gear 123e and the second inner ring gear 223e is different.

[0097]

[0023] Because at least one pair of symmetrically arranged gears of the first gear transmission 12e and the second gear transmission 22e has a different number of teeth, the first gear transmission 12e and the second gear transmission 22e are not completely symmetrical, which realizes order separation between the first gear transmission 12e and the second gear transmission 22e and further prevents order overlap between the first gear transmission 12e and the second gear transmission 22e. This significantly reduces order noise when the first gear transmission 12e and the second gear transmission 22e operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride. Furthermore, the first motor 11e and the second motor 21e can be low-power motors. When the first motor 11e and the second motor 21e operate simultaneously, the dual-motor electric drive assembly 100e can output high power, thereby meeting the high-power requirements of the vehicle. Because the first motor 11e and the second motor 21e can be controlled independently, the power output of one or both sides can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control of the vehicle to be realized, resulting in more accurate control. For example, by controlling the rotation speed and torque of the first motor 11e and the second motor 21e, respectively, differential speed and torque distribution between the wheels can be realized, allowing the vehicle to travel in a straight line.

[0098] In one exemplary embodiment, the first sun gear 121e and the second sun gear 221e have different numbers of teeth, the first planetary gear 122e and the third planetary gear 222e have different numbers of teeth, the second planetary gear 125e and the fourth planetary gear 225e have different numbers of teeth, and the first inner ring gear 123e and the second inner ring gear 223e have different numbers of teeth.

[0099] In this way, the number of teeth between all symmetrically arranged gears is different, which further reduces harmonic noise when the first gear transmission mechanism 12e and the second gear transmission mechanism 22e operate simultaneously, improving the NVH performance of the automobile and providing a more comfortable ride.

[0100] Example 7 As shown in Figure 7, Figure 7 illustrates the structure of a dual motor electric drive assembly 100f in Example 7. The dual motor electric drive assembly 100f is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a purely electric vehicle.

[0101] The dual motor electric drive assembly 100f includes a first drive mechanism 1f and a second drive mechanism 2f. The first drive mechanism 1f and the second drive mechanism 2f may be mounted on the same transaxle. The first drive mechanism 1f includes a first motor 11f, a first gear transmission 12f, and a first driver shaft 13f. The first gear transmission 12f is mounted between the first driver shaft 13f and the first motor 11f. A main shaft of the first motor 11f is connected to the first gear transmission 12f, which in turn is connected to the first driver shaft 13f. The first gear transmission 12f may be a reducer, which can increase the torque output by the first motor 11f by reducing the speed before transmitting it to the first driver shaft 13f to rotate the first driver shaft 13f.

[0102] The second drive mechanism 2f includes a second motor 21f, a second gear transmission 22f, and a second driver shaft 23f. The second gear transmission 22f is disposed between the second driver shaft 23f and the second motor 21f. The main shaft of the second motor 21f is connected to the second gear transmission 22f, and the first gear transmission 12f is connected to the second driver shaft 23f. The second gear transmission 22f may be a reducer, which can increase the torque output by the second motor 21f by reducing the speed and then transmit it to the second driver shaft 23f to rotate the second driver shaft 23f. The first motor 11f and the second motor 21f are provided between the first gear transmission mechanism 12f and the second gear transmission mechanism 22f, the first driver shaft 13f is provided on the side of the first gear transmission mechanism 12f opposite the second gear transmission mechanism 22f, and the second driver shaft 23f is provided on the side of the second gear transmission mechanism 22f opposite the first gear transmission mechanism 12f. The first driver shaft 13f, the second driver shaft 23f, the main shaft of the first motor 11f, and the main shaft of the second motor 21f are provided coaxially.

[0103] In this embodiment, the first gear transmission mechanism 12f is configured as a horizontal double-row planetary gear mechanism. The first gear transmission mechanism 12f includes a first sun gear 121f, a first planetary gear 122f, a second planetary gear 125f, a first inner ring gear 123f, and a first planet carrier 124f. The first inner ring gear 123f is fixed and cannot move. The first sun gear 121f is located on the side of the first inner ring gear 123f closer to the first motor 11f and is coaxial with the first inner ring gear 123f. The outer diameter of the first sun gear 121f is smaller than the inner diameter of the first inner ring gear 123f. The main shaft of the first motor 11f is coaxial with the first sun gear 121f, and the first sun gear 121f is fitted onto the main shaft of the first motor 11f.

[0104] The axes of the first planetary gear 122f and the second planetary gear 125f are both parallel to the axis of the first sun gear 121f. A plurality of first planetary gears 122f, for example, three, may be provided, and the plurality of first planetary gears 122f are evenly distributed in the circumferential direction of the first sun gear 121f. The plurality of first planetary gears 122f mesh with the first sun gear 121f. The number of second planetary gears 125f is the same as the number of first planetary gears 122f. The first planetary gears 122f are provided in one-to-one correspondence with the second planetary gears 125f. The second planetary gears 125f are provided coaxially with the corresponding first planetary gears 122f and mesh with the first inner ring gear 123f. The outer diameter of the first planetary gears 122f is larger than the outer diameter of the second planetary gears 125f.

[0105] The first planetary carrier 124f includes a first holder 1241f and a first rotation shaft 1242f. The first holder 1241f is provided on the opposite side of the second planetary gear 125f from the first planetary gear 122f. The first rotation shaft 1242f is parallel to the axis of the first sun gear 121f, and one end of the first rotation shaft 1242f is connected to the first holder 1241f. The number of first rotation shafts 1242f is the same as the number of first planetary gears 122f, the first rotation shafts 1242f are provided in one-to-one correspondence with the first planetary gears 122f, the first rotation shafts 1242f are provided in one-to-one correspondence with the second planetary gears 125f, the first planetary gears 122f are fitted onto the corresponding first rotation shafts 1242f and are rotatable about the first rotation shafts 1242f, and the second planetary gears 125f are fitted onto the corresponding first rotation shafts 1242f and are rotatable about the first rotation shafts 1242f. The first driver shaft 13f is provided on the side of the first holder 1241f opposite to the first sun gear 121f and is arranged so as to be coaxial with the first sun gear 121f. One end of the first driver shaft 13f is connected to a first holder 1241f of the first planetary carrier 124f.

[0106] The torque output from the main shaft of the first motor 11f is transmitted to the first driver shaft 13f via the first gear transmission mechanism 12f, thereby driving the first driver shaft 13f to rotate.

[0107] In this embodiment, the second gear transmission mechanism 22f is configured as a horizontal double-row planetary gear mechanism. The second gear transmission mechanism 22f includes a second sun gear 221f, a third planetary gear 222f, a fourth planetary gear 225f, a second inner ring gear 223f, and a second planet carrier 224f. The second inner ring gear 223f is fixed and cannot move. The second sun gear 221f is located on the side of the second inner ring gear 223f closer to the second motor 21f and is coaxial with the second inner ring gear 223f. The outer diameter of the second sun gear 221f is smaller than the inner diameter of the second inner ring gear 223f. The main shaft of the second motor 21f is coaxial with the second sun gear 221f, and the second sun gear 221f is fitted onto the main shaft of the second motor 21f.

[0108] The axes of the third planetary gear 222f and the fourth planetary gear 225f are both parallel to the axis of the second sun gear 221f. A plurality of third planetary gears 222f, for example, three, may be provided, and the plurality of third planetary gears 222f are evenly distributed in the circumferential direction of the second sun gear 221f. All of the plurality of third planetary gears 222f mesh with the second sun gear 221f. The number of fourth planetary gears 225f is the same as the number of third planetary gears 222f. The third planetary gears 222f are provided in one-to-one correspondence with the fourth planetary gears 225f. All of the fourth planetary gears 225f are provided within the second inner ring gear 223f. The fourth planetary gears 225f are provided coaxially with the corresponding third planetary gears 222f and mesh with the second inner ring gear 223f. The outer diameter of the third planetary gear 222f is larger than the outer diameter of the fourth planetary gear 225f.

[0109] The second planetary carrier 224f includes a second holder 2241f and a second rotation shaft 2242f. The second holder 2241f is provided on the opposite side of the fourth planetary gear 225f from the third planetary gear 222f. The second rotation shaft 2242f is parallel to the axis of the second sun gear 221f, and one end of the second rotation shaft 2242f is connected to the second holder 2241f. The number of second rotation shafts 2242f is the same as the number of third planetary gears 222f, the second rotation shafts 2242f are provided in one-to-one correspondence with the third planetary gears 222f, the second rotation shafts 2242f are provided in one-to-one correspondence with the fourth planetary gears 225f, the third planetary gears 222f are fitted onto the corresponding second rotation shafts 2242f and are rotatable about the second rotation shafts 2242f, and the fourth planetary gears 225f are fitted onto the corresponding second rotation shafts 2242f and are rotatable about the second rotation shafts 2242f. The second driver shaft 23f is provided on the side of the second holder 2241f opposite the second sun gear 221f and is arranged so as to be coaxial with the second sun gear 221f. One end of the second driver shaft 23f is connected to the second holder 2241f of the second planetary carrier 224f.

[0110] The torque output from the main shaft of the second motor 21f is transmitted to the second driver shaft 23f via the second gear transmission mechanism 22f, thereby driving the second driver shaft 23f to rotate.

[0111] Since the first gear transmission mechanism 12f and the second gear transmission mechanism 22f are both horizontal double-row planetary gear mechanisms, the transmission ratios of the first gear transmission mechanism 12f and the second gear transmission mechanism 22f are both greater than the transmission ratio of a single-row planetary gear mechanism. In addition, the radial dimension of the horizontal double-row planetary gear mechanism is smaller than that of a vertical double-row planetary gear mechanism.

[0112] The first sun gear 121f and the second sun gear 221f are arranged symmetrically, the first planetary gear 122f and the third planetary gear 222f are arranged symmetrically, the second planetary gear 125f and the fourth planetary gear 225f are arranged symmetrically, the first inner ring gear 123f and the second inner ring gear 223f are arranged symmetrically, and the first planetary carrier 124f and the second planetary carrier 224f are arranged symmetrically.

[0113] At least one of the numbers of teeth of the first sun gear 121f and the second sun gear 221f, the first planetary gear 122f and the third planetary gear 222f, the second planetary gear 125f and the fourth planetary gear 225f, and the first inner ring gear 123f and the second inner ring gear 223f is different.

[0114]

[0023] Because at least one pair of symmetrically arranged gears among the first gear transmission 12f and the second gear transmission 22f has a different number of teeth, the first gear transmission 12f and the second gear transmission 22f are not completely symmetrical, which realizes order separation between the first gear transmission 12f and the second gear transmission 22f and further prevents order overlap between the first gear transmission 12f and the second gear transmission 22f. This significantly reduces order noise when the first gear transmission 12f and the second gear transmission 22f operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride. Furthermore, the first motor 11f and the second motor 21f may be low-power motors. When the first motor 11f and the second motor 21f operate simultaneously, the dual-motor electric drive assembly 100f can output high power, thereby meeting the high-power requirements of the vehicle. Because the first motor 11f and the second motor 21f can be controlled independently, the power output of one or both sides can be changed according to power requirements, realizing functions such as differential, differential lock, and vector control for the vehicle, and enabling more accurate control. For example, by controlling the rotation speed and torque of the first motor 11f and the second motor 21f, respectively, differential speed and torque distribution between the wheels can be realized, allowing the vehicle to travel in a straight line.

[0115] In one exemplary embodiment, the first sun gear 121f and the second sun gear 221f have different numbers of teeth, the first planetary gear 122f and the third planetary gear 222f have different numbers of teeth, the second planetary gear 125f and the fourth planetary gear 225f have different numbers of teeth, and the first inner ring gear 123f and the second inner ring gear 223f have different numbers of teeth.

[0116] In this way, the number of teeth between all symmetrically arranged gears is different, which further reduces harmonic noise when the first gear transmission mechanism 12f and the second gear transmission mechanism 22f operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride.

[0117] Example 8 As shown in Figure 8, Figure 8 shows the structure of a dual motor electric drive assembly 100g in Example 8. The dual motor electric drive assembly 100g is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a pure electric vehicle.

[0118] The dual motor electric drive assembly 100g includes a first drive mechanism 1g and a second drive mechanism 2g. The first drive mechanism 1g and the second drive mechanism 2g may be mounted on the same transaxle. The first drive mechanism 1g includes a first motor 11g, a first gear transmission 12g, and a first driver shaft 13g. The first gear transmission 12g is mounted between the first driver shaft 13g and the first motor 11g. A main shaft of the first motor 11g is connected to the first gear transmission 12g, which in turn is connected to the first driver shaft 13g. The first gear transmission 12g may be a reducer, which can increase the torque output by the first motor 11g by reducing the speed before transmitting it to the first driver shaft 13g to rotate the first driver shaft 13g.

[0119] The second drive mechanism 2g includes a second motor 21g, a second gear transmission 22g, and a second driver shaft 23g. The second gear transmission 22g is disposed between the second driver shaft 23g and the second motor 21g. The main shaft of the second motor 21g is connected to the second gear transmission 22g, and the first gear transmission 12g is connected to the second driver shaft 23g. The second gear transmission 22g may be a reducer, which can increase the torque output by the second motor 21g by reducing the speed and then transmit it to the second driver shaft 23g to rotate the second driver shaft 23g. The first motor 11g and the second motor 21g are provided between the first gear transmission mechanism 12g and the second gear transmission mechanism 22g, the first driver shaft 13g is provided on the side of the first gear transmission mechanism 12g opposite to the second gear transmission mechanism 22g, and the second driver shaft 23g is provided on the side of the second gear transmission mechanism 22g opposite to the first gear transmission mechanism 12g. The first driver shaft 13g, the second driver shaft 23g, the main shaft of the first motor 11g, and the main shaft of the second motor 21g are provided coaxially.

[0120] In this embodiment, the first gear transmission mechanism 12g is configured as a horizontal double-row planetary gear mechanism. The first gear transmission mechanism 12g includes a first sun gear 121g, a second sun gear 123g, a first planetary gear 122g, a second planetary gear 125g, and a first planetary carrier 124g. The first sun gear 121g is fitted onto the main shaft of the first motor 11g. The second sun gear 123g is provided on the side of the first sun gear 121g opposite the first motor 11g. The second sun gear 123g is provided coaxially with the first sun gear 121g. The second sun gear 123g is provided fixedly. The second sun gear 123g may be fixedly fitted onto a single rotation shaft, which is provided coaxially with the first sun gear 121g, and the second sun gear 123g cannot rotate around the rotation shaft. The outer diameter of the second sun gear 123g may be larger than the outer diameter of the first sun gear 121g.

[0121] The axes of the first planetary gear 122g and the second planetary gear 125g are both parallel to the axis of the first sun gear 121g. A plurality of first planetary gears 122g, for example, three, may be provided, and the plurality of first planetary gears 122g are evenly distributed in the circumferential direction of the first sun gear 121g. The plurality of first planetary gears 122g mesh with the first sun gear 121g. The number of second planetary gears 125g is the same as the number of first planetary gears 122g. The plurality of second planetary gears 125g are evenly distributed in the circumferential direction of the second sun gear 123g. The first planetary gears 122g are provided in one-to-one correspondence with the second planetary gears 125g. The second planetary gears 125g are provided coaxially with their corresponding first planetary gears 122g and mesh with the second sun gear 123g. The outer diameter of the first planetary gear 122g is larger than the outer diameter of the second planetary gear 125g.

[0122] The first planetary carrier 124g includes a first holder 1241g and a first rotation shaft 1242g. The first holder 1241g is provided on the opposite side of the second planetary gear 125g from the first planetary gear 122g. The first rotation shaft 1242g is parallel to the axis of the first sun gear 121g, and one end of the first rotation shaft 1242g is connected to the first holder 1241g. The number of first rotation shafts 1242g is the same as the number of first planetary gears 122g, the first rotation shafts 1242g are provided in one-to-one correspondence with the first planetary gears 122g, the first rotation shafts 1242g are provided in one-to-one correspondence with the second planetary gears 125g, the first planetary gears 122g are fitted onto the corresponding first rotation shafts 1242g and are rotatable about the first rotation shafts 1242g, and the second planetary gears 125g are fitted onto the corresponding first rotation shafts 1242g and are rotatable about the first rotation shafts 1242g. The first driver shaft 13g is provided on the side of the first holder 1241g opposite to the second sun gear 123g and is arranged so as to be coaxial with the second sun gear 123g. One end of the first driver shaft 13g is connected to a first holder 1241g of the first planetary carrier 124g.

[0123] Torque output from the main shaft of the first motor 11g is sent to the first driver shaft 13g via the first gear transmission mechanism 12g, thereby driving the first driver shaft 13g to rotate.

[0124] In this embodiment, the second gear transmission mechanism 22g is configured as a horizontal double-row planetary gear mechanism. The second gear transmission mechanism 22g includes a third sun gear 221g, a fourth sun gear 223g, a third planetary gear 222g, a fourth planetary gear 225g, and a second planet carrier 224g. The third sun gear 221g is fitted onto the main shaft of the second motor 21g. The fourth sun gear 223g is provided on the opposite side of the third sun gear 221g from the second motor 21g. The fourth sun gear 223g is provided coaxially with the third sun gear 221g. The fourth sun gear 223g is provided fixedly. The fourth sun gear 223g may be fixedly fitted onto a single rotation shaft, which is provided coaxially with the fourth sun gear 223g, and the fourth sun gear 223g cannot rotate around the rotation shaft. The outer diameter of the fourth sun gear 223g may be larger than the outer diameter of the third sun gear 221g.

[0125] The axes of the third planetary gear 222g and the fourth planetary gear 225g are both parallel to the axis of the third sun gear 221g. A plurality of third planetary gears 222g, for example, three, may be provided, and the plurality of third planetary gears 222g are evenly distributed in the circumferential direction of the third sun gear 221g. All of the plurality of third planetary gears 222g mesh with the third sun gear 221g. The number of fourth planetary gears 225g is the same as the number of third planetary gears 222g. The plurality of fourth planetary gears 225g are evenly distributed in the circumferential direction of the fourth sun gear 223g. The third planetary gears 222g are provided in one-to-one correspondence with the fourth planetary gears 225g. The fourth planetary gears 225g are provided coaxially with the corresponding third planetary gears 222g and mesh with the fourth sun gear 223g. The outer diameter of the third planetary gear 222g is larger than the outer diameter of the fourth planetary gear 225g.

[0126] The second planet carrier 224g includes a second holder 2241g and a second rotation shaft 2242g. The second holder 2241g is provided on the opposite side of the fourth planetary gear 225g from the third planetary gear 222g. The second rotation shaft 2242g is parallel to the axis of the third sun gear 221g, and one end of the second rotation shaft 2242g is connected to the second holder 2241g. The second rotation shafts 2242g are the same in number as the third planetary gears 222g, the second rotation shafts 2242g are provided in one-to-one correspondence with the third planetary gears 222g, the second rotation shafts 2242g are provided in one-to-one correspondence with the fourth planetary gears 225g, the third planetary gears 222g are fitted onto the corresponding second rotation shafts 2242g and are rotatable about the second rotation shafts 2242g, and the fourth planetary gears 225g are fitted onto the corresponding second rotation shafts 2242g and are rotatable about the second rotation shafts 2242g. The second driver shaft 23g is provided on the side of the second holder 2241g opposite to the second sun gear 123g, and is arranged so as to be coaxial with the third sun gear 221g. One end of the second driver shaft 23g is connected to the second holder 2241g of the second planetary carrier 224g.

[0127] The torque output from the main shaft of the second motor 21g is sent to the second driver shaft 23g via the second gear transmission mechanism 22g, thereby driving the second driver shaft 23g to rotate.

[0128] The first gear transmission mechanism 12g and the second gear transmission mechanism 22g are both horizontal double-row planetary gear mechanisms, and therefore the transmission ratios of the first gear transmission mechanism 12g and the second gear transmission mechanism 22g are both greater than that of a single-row planetary gear mechanism. Furthermore, the first gear transmission mechanism 12g and the second gear transmission mechanism 22g in this embodiment do not have inner ring gears, but use second sun gear 123g and fourth sun gear 223g instead, resulting in a more compact structure and lower manufacturing costs.

[0129] The first sun gear 121g and the third sun gear 221g are arranged symmetrically, the second sun gear 123g and the fourth sun gear 223g are arranged symmetrically, the first planetary gear 122g and the third planetary gear 222g are arranged symmetrically, the second planetary gear 125g and the fourth planetary gear 225g are arranged symmetrically, and the first planetary carrier 124g and the second planetary carrier 224g are arranged symmetrically. At least one of the numbers of teeth of the first sun gear 121g and the third sun gear 221g, the second sun gear 123g and the fourth sun gear 223g, the first planetary gear 122g and the third planetary gear 222g, and the second planetary gear 125g and the fourth planetary gear 225g is different.

[0130]

[0023] Because at least one pair of symmetrically arranged gears in the first gear transmission 12g and the second gear transmission 22g has a different number of teeth, the first gear transmission 12g and the second gear transmission 22g are not completely symmetrical, which achieves order separation between the first gear transmission 12g and the second gear transmission 22g and further prevents order overlap between the first gear transmission 12g and the second gear transmission 22g. This significantly reduces order noise when the first gear transmission 12g and the second gear transmission 22g operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride. Furthermore, the first motor 11g and the second motor 21g may be low-power motors. When the first motor 11g and the second motor 21g operate simultaneously, the dual-motor electric drive assembly 100g can output high power, thereby meeting the high-power requirements of the vehicle. Because the first motor 11g and the second motor 21g can be controlled independently, the power output of one or both sides can be changed according to power requirements, realizing functions such as differential, differential lock, and vector control for the vehicle, allowing for more accurate control. For example, by controlling the rotation speed and torque of the first motor 11g and the second motor 21g, respectively, differential speed and torque distribution between the wheels can be realized, allowing the vehicle to travel in a straight line.

[0131] In one exemplary embodiment, the first sun gear 121g and the third sun gear 221g have different numbers of teeth, the second sun gear 123g and the fourth sun gear 223g have different numbers of teeth, the first planetary gear 122g and the third planetary gear 222g have different numbers of teeth, and the second planetary gear 125g and the fourth planetary gear 225g have different numbers of teeth.

[0132] In this way, the number of teeth between all symmetrically arranged gears is different, which further reduces harmonic noise when the first gear transmission mechanism 12g and the second gear transmission mechanism 22g operate simultaneously, improving the NVH performance of the automobile and providing a more comfortable ride.

[0133] Example 9 As shown in Figure 9, Figure 9 illustrates the structure of a dual motor electric drive assembly 100h in Example 9. The dual motor electric drive assembly 100h is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a pure electric vehicle.

[0134] The dual motor electric drive assembly 100h includes a first drive mechanism 1 and a second drive mechanism 2a. The first drive mechanism 1 and the second drive mechanism 2a may be provided on the same transaxle.

[0135] The first drive mechanism 1 includes a first motor 11, a first planetary gear mechanism 12, and a first driver shaft 13. The first planetary gear mechanism 12 is provided between the first driver shaft 13 and the first motor 11. A main shaft of the first motor 11 is connected to the first planetary gear mechanism 12, which is connected to the first driver shaft 13. The first planetary gear mechanism 12 may be a reducer, and the first planetary gear mechanism 12 can increase the torque output by the first motor 11 by reducing the speed before sending it to the first driver shaft 13 to rotate the first driver shaft 13.

[0136] The second drive mechanism 2a includes a second motor 21a, a second planetary gear mechanism 22a, and a second driver shaft 23a. The second planetary gear mechanism 22a is disposed between the second driver shaft 23a and the second motor 21a. The main shaft of the second motor 21a is connected to the second planetary gear mechanism 22a, and the first planetary gear mechanism 12a is connected to the second driver shaft 23a. The second planetary gear mechanism 22a may be a reducer, and the second planetary gear mechanism 22a can increase the torque output by the second motor 21a by reducing the speed before transmitting it to the second driver shaft 23a to rotate the second driver shaft 23a.

[0137] The first motor 11 and the second motor 21a are provided between the first planetary gear mechanism 12 and the second planetary gear mechanism 22a, the first driver shaft 13 is provided on the side of the first planetary gear mechanism 12 opposite to the second planetary gear mechanism 22a, and the second driver shaft 23a is provided on the side of the second planetary gear mechanism 22a opposite to the first planetary gear mechanism 12. The first driver shaft 13, the second driver shaft 23, the main shaft of the first motor 11, and the main shaft of the second motor 21a are provided coaxially.

[0138] In this embodiment, the first planetary gear mechanism 1 and the second planetary gear mechanism 2a have different gear arrangement methods.

[0139] The first planetary gear mechanism 12 and the second planetary gear mechanism 22a have different gear arrangements, which separate the gear orders of the first planetary gear mechanism 12 and the second planetary gear mechanism 22a. This avoids overlapping of the gear orders between the first planetary gear mechanism 12 and the second planetary gear mechanism 22a. This significantly reduces the order noise generated when the first planetary gear mechanism 12 and the second planetary gear mechanism 22a operate simultaneously, improving the vehicle's NVH performance and providing a more comfortable ride. Furthermore, the first motor 11 and the second motor 21a can be low-power motors. When the first motor 11 and the second motor 21a operate simultaneously, the dual-motor electric drive assembly 100h can output high power, meeting the high-power requirements of the vehicle. Because the first motor 11 and the second motor 21a can be controlled independently, the power output of one or both motors can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control for the vehicle, resulting in more accurate control. For example, by controlling the rotation speed and torque of the first motor 11 and the second motor 21a, respectively, differential speed and torque distribution between the wheels can be achieved, allowing the car to travel in a straight line.

[0140] In one exemplary embodiment, the first drive mechanism 1 is a single-row planetary gear mechanism, and the second planetary gear mechanism 2a is a double-row planetary gear mechanism.

[0141] In this embodiment, the first planetary gear mechanism 12 includes a first sun gear 121, a first planetary gear 122, a first inner ring gear 123, a first planetary carrier 124, and a sun gear rotation shaft 120. The first inner ring gear 123 is provided coaxially with the main shaft of the first motor 11. The first inner ring gear 123 includes a connecting member 1232 and a ring gear body 1231. The ring gear body 1231 is configured in a ring shape. The connecting member 1232 is provided at an end of the ring gear body 1231 close to the first motor 11. The connecting member 1232 connects the ring gear body 1231 to the main shaft of the first motor 11. The sun gear rotation shaft 120 is provided within the ring gear body 1231 and is provided coaxially with the first inner ring gear 123. The first sun gear 121 is disposed within the first inner ring gear 123, is disposed coaxially with the first inner ring gear 123, and is fixedly fitted to the sun gear rotation axis 120. The first sun gear 121 cannot rotate around the sun gear rotation axis 120. An annular gap exists between the first sun gear 121 and the first inner ring gear 123. The first planetary gears 122 are disposed within the annular gap between the first sun gear 121 and the first inner ring gear 123. The axis of the first planetary gears 122 is parallel to the axis of the first sun gear 121.

[0142] The first sun gear 121 and the first inner ring gear 123 both mesh with the first planetary gears 122. A plurality of first planetary gears 122, for example, three, may be provided, and the plurality of first planetary gears 122 are evenly distributed in the circumferential direction of the first sun gear 121. The first planet carrier 124 includes a first holder 1241 and a first rotating shaft 1242. The first holder 1241 is provided on the side of the first sun gear 121 opposite to the first motor 11. The first rotating shaft 1242 is parallel to the axis of the first sun gear 121, and one end of the first rotating shaft 1242 is connected to the first holder 1241. The number of first rotating shafts 1242 is the same as the number of first planetary gears 122, and the first rotating shafts 1242 are provided in one-to-one correspondence with the first planetary gears 122, and the first planetary gears 122 are fitted onto the corresponding first rotating shafts 1242 and are rotatable around the first rotating shafts 1242. The first driver shaft 13 is provided on the side of the first holder 1241 opposite to the first sun gear 121, and is provided so as to be coaxial with the first sun gear 121. One end of the first driver shaft 13 is connected to the first holder 1241 of the first planetary carrier 124.

[0143] In this embodiment, the second planetary gear mechanism 22a is configured as a vertical double-row planetary gear mechanism. The second planetary gear mechanism 22a includes a second sun gear 221a, a third planetary gear 222a, a fourth planetary gear 225a, a second inner ring gear 223a, and a second planet carrier 224a. The second inner ring gear 223a is fixed and cannot move. The second sun gear 221a is disposed within the second inner ring gear 223a and is coaxial with the second inner ring gear 223a. The main shaft of the second motor 21a is coaxial with the second sun gear 221a, and the second sun gear 221a is fitted onto the main shaft of the second motor 21a. An annular gap exists between the second sun gear 221a and the second inner ring gear 223a. The third planetary gear 222a and the fourth planetary gear 225a are both disposed in the annular gap between the second sun gear 221a and the second inner ring gear 223a. The axes of the third planetary gear 222a and the fourth planetary gear 225a are both parallel to the axis of the second sun gear 221a. A plurality of third planetary gears 222a, for example, three, may be provided, and the plurality of third planetary gears 222a are evenly distributed in the circumferential direction of the second sun gear 221a. The plurality of third planetary gears 222a mesh with the second sun gear 221a. The number of fourth planetary gears 225a is the same as the number of third planetary gears 222a. The third planetary gears 222a are disposed in one-to-one correspondence with the fourth planetary gears 225a. The third planetary gears 222a mesh with the corresponding fourth planetary gears 225a and also mesh with the second inner ring gear 223a.

[0144] The second planetary carrier 224a includes a second holder 2241a, a third rotation shaft 2242a, and a fourth rotation shaft 2243a. The second holder 2241a is provided on the side of the second sun gear 221a opposite the second motor 21a. The third rotation shaft 2242a and the fourth rotation shaft 2243a are both parallel to the axis of the second sun gear 221a, and one end of each of the third rotation shaft 2242a and the fourth rotation shaft 2243a is connected to the first holder 1241a. The number of third rotation shafts 2242a is the same as the number of third planetary gears 222a, and the third rotation shafts 2242a are provided in one-to-one correspondence with the third planetary gears 222a. The third planetary gears 222a are fitted onto the corresponding third rotation shafts 2242a and are rotatable about the third rotation shafts 2242a. The number of fourth rotation shafts 2243a is the same as the number of fourth planetary gears 225a, and the fourth rotation shafts 2243a are provided in one-to-one correspondence with the fourth planetary gears 225a. The fourth planetary gears 225a are fitted onto the corresponding fourth rotation shafts 2243a and can rotate around the fourth rotation shafts 2243a. The second driver shaft 23a is provided on the side of the second holder 2241a opposite the second sun gear 221a and is provided coaxially with the second sun gear 221a. One end of the second driver shaft 23a is connected to the second holder 2241a of the second planetary carrier 224a.

[0145] The torque output from the main shaft of the second motor 21a is transmitted to the second driver shaft 23a via the second sun gear 221a, the third planetary gear 222a, the fourth planetary gear 225a, the second inner ring gear 223a, and the second planetary carrier 224a in that order, thereby driving the second driver shaft 23a to rotate.

[0146] The first planetary gear mechanism 12 is a single-row planetary gear mechanism, and the second planetary gear mechanism 22a is a double-row planetary gear mechanism. The transmission ratio of the second planetary gear mechanism 22a is greater than that of the first planetary gear mechanism 12.

[0147] Because the first planetary gear mechanism 12 and the second planetary gear mechanism 22a are different types of planetary gear mechanisms, the gear arrangement methods of the first planetary gear mechanism 12 and the second planetary gear mechanism 22a are different and the torque is transmitted through different paths between them, which achieves order separation of the first planetary gear mechanism 12 and the second planetary gear mechanism 22a and further prevents the orders of the first planetary gear mechanism 12 and the second planetary gear mechanism 22a from overlapping. This significantly reduces order noise when the first planetary gear mechanism 12 and the second planetary gear mechanism 22a operate simultaneously, improves the NVH performance of the vehicle, and provides a more comfortable ride.

[0148] In one exemplary embodiment, the first driver shaft 13, the first planetary gear mechanism 12, the first motor 11, the second motor 21a, the second planetary gear mechanism 22a, and the second driver shaft 23a are arranged in sequence and coaxially.

[0149] When arranged in this manner, the dual motor electric drive assembly can extend along the transaxle and has small radial dimensions, a compact structure, and a small space footprint.

[0150] Example 10 As shown in Figure 10, Figure 10 illustrates the structure of a dual motor electric drive assembly 100i in Example 10. The dual motor electric drive assembly 100i is attached to a vehicle and provides power for the vehicle to run. The vehicle may be a purely electric vehicle.

[0151] The dual motor electric drive assembly 100i includes a first drive mechanism 1a and a second drive mechanism 2b, which may be mounted on the same transaxle.

[0152] The first drive mechanism 1a includes a first motor 11a, a first planetary gear mechanism 12a, and a first driver shaft 13a. The first planetary gear mechanism 12a is disposed between the first driver shaft 13a and the first motor 11a. A main shaft of the first motor 11a is connected to the first planetary gear mechanism 12a, which is connected to the first driver shaft 13a. The first planetary gear mechanism 12a may be a reducer, which can increase the torque output by the first motor 11a by reducing the speed before transmitting it to the first driver shaft 13a to rotate the first driver shaft 13a.

[0153] The second drive mechanism 2b includes a second motor 21b, a second planetary gear mechanism 22b, and a second driver shaft 23b. The second planetary gear mechanism 22b is disposed between the second driver shaft 23b and the second motor 21b. The main shaft of the second motor 21b is connected to the second planetary gear mechanism 22b, and the first planetary gear mechanism 12b is connected to the second driver shaft 23b. The second planetary gear mechanism 22b may be a reducer, and the second planetary gear mechanism 22b can increase the torque output by the second motor 21b by reducing the speed before transmitting it to the second driver shaft 23b to rotate the second driver shaft 23b.

[0154] The first motor 11a and the second motor 21b are provided between the first planetary gear mechanism 12a and the second planetary gear mechanism 22b, the first driver shaft 13a is provided on the side of the first planetary gear mechanism 12a opposite to the second planetary gear mechanism 22b, and the second driver shaft 23b is provided on the side of the second planetary gear mechanism 22b opposite to the first planetary gear mechanism 12a. The first driver shaft 13a, the second driver shaft 23b, the main shaft of the first motor 11a, and the main shaft of the second motor 21b are provided coaxially.

[0155] In this embodiment, the first planetary gear mechanism 12a is configured as a vertical double-row planetary gear mechanism. The first planetary gear mechanism 12a includes a first sun gear 121a, a first planetary gear 122a, a second planetary gear 125a, a first inner ring gear 123a, a first planet carrier 124a, and a sun gear rotation shaft 120a. The first inner ring gear 123a is arranged coaxially with the main shaft of the first motor 11a. The first inner ring gear 123a includes a connecting member 1232a and a ring gear main body 1231a. The connecting member 1232a is arranged at an end of the ring gear main body 1231a closer to the first motor 11a. The connecting member 1232a connects the ring gear main body 1231a to the main shaft of the first motor 11a. The sun gear rotation shaft 120a is provided within the first inner ring gear 123a and is coaxial with the first inner ring gear 123a. The first sun gear 121a is provided within the first inner ring gear 123a and is coaxial with the first inner ring gear 123a, and is fixedly fitted to the sun gear rotation shaft 120a. The first sun gear 121a cannot rotate around the sun gear rotation shaft 120a. An annular gap exists between the first sun gear 121a and the first inner ring gear 123a. The first planetary gear 122a and the second planetary gear 125a are both provided within the annular gap between the first sun gear 121a and the first inner ring gear 123a. The axes of the first planetary gear 122a and the second planetary gear 125a are both parallel to the axis of the first sun gear 121a. A plurality of first planetary gears 122a, for example, three, may be provided, and the plurality of first planetary gears 122a are evenly distributed in the circumferential direction of the first sun gear 121a. The plurality of first planetary gears 122a mesh with the first sun gear 121a. The number of second planetary gears 125a is the same as the number of first planetary gears 122a. The first planetary gears 122a are provided in one-to-one correspondence with the second planetary gears 125a. The second planetary gears 125a mesh with the corresponding first planetary gears 122a and also mesh with the first inner ring gear 123a.

[0156] The first planetary carrier 124a includes a first holder 1241a, a first rotating shaft 1242a, and a second rotating shaft 1243a. The first holder 1241a is provided on the side of the first sun gear 121a opposite the first motor 11a. The first rotating shaft 1242a and the second rotating shaft 1243a are both parallel to the axis of the first sun gear 121a, and one end of each of the first rotating shaft 1242a and the second rotating shaft 1243a is connected to the first holder 1241a. The number of first rotating shafts 1242a is the same as the number of first planetary gears 122a, and the first rotating shafts 1242a are provided in one-to-one correspondence with the first planetary gears 122a. The first planetary gears 122a are fitted onto the corresponding first rotating shafts 1242a and are rotatable about the first rotating shafts 1242a. The number of second rotating shafts 1243a is the same as the number of second planetary gears 125a, and the second rotating shafts 1243a are provided in one-to-one correspondence with the second planetary gears 125a. The second planetary gears 125a are fitted onto the corresponding second rotating shafts 1243a and are rotatable about the second rotating shafts 1243a. The first driver shaft 13a is provided on the side of the first holder 1241a opposite to the first sun gear 121a, and is provided coaxially with the first sun gear 121a. One end of the first driver shaft 13a is connected to the first holder 1241a of the first planetary carrier 124a.

[0157] The torque output from the main shaft of the first motor 11a is transmitted to the first driver shaft 13a via the first sun gear 121a, the first planetary gear 122a, the second planetary gear 125a, the first inner ring gear 123a, and the first planetary carrier 124a in that order, thereby driving the first driver shaft 13a to rotate.

[0158] In this embodiment, the second planetary gear mechanism 22b is configured as a horizontal double-row planetary gear mechanism. The second planetary gear mechanism 22b includes a second sun gear 221b, a third planetary gear 222b, a fourth planetary gear 225b, a second inner ring gear 223b, a second planet carrier 224b, and a sun gear rotation shaft 220b. The second inner ring gear 223b is provided coaxially with the main shaft of the second motor 21b. The second inner ring gear 223b includes a connecting member 2232b and a ring gear main body 2231b. The connecting member 2232b is provided at one end of the ring gear main body 2231b. The connecting member 2232b is connected to the ring gear main body 2231b and the main shaft of the second motor 21b, respectively. The connecting member 2232b may be provided at one end of the ring gear main body 2231b. The sun gear rotation shaft 220b is provided on the opposite side of the second inner ring gear 223b from the second motor 21b, and is coaxial with the second inner ring gear 223b, and the sun gear rotation shaft 220b is fixedly provided. The second sun gear 221b is fixedly fitted onto the sun gear rotation shaft 220b, and the second sun gear 221b cannot rotate around the sun gear rotation shaft 220b. In this way, the second sun gear 221b is provided on the opposite side of the second inner ring gear 223b from the second motor 21b, and is coaxial with the second inner ring gear 223b, and the outer diameter of the second sun gear 221b is smaller than the inner diameter of the second inner ring gear 223b.

[0159] The axes of the third planetary gear 222b and the fourth planetary gear 225b are both parallel to the axis of the second sun gear 221b. A plurality of third planetary gears 222b, for example three, may be provided, and the plurality of third planetary gears 222b are evenly distributed in the circumferential direction of the second sun gear 221b. All of the plurality of third planetary gears 222b mesh with the second sun gear 221b. The fourth planetary gears 225b are provided inside the second inner ring gear 223b. The number of fourth planetary gears 225b is the same as the number of third planetary gears 222b. The third planetary gears 222b are provided in one-to-one correspondence with the fourth planetary gears 225b. All of the fourth planetary gears 225b are provided within the second inner ring gear 223b. The fourth planetary gear 225b is provided coaxially with the corresponding third planetary gear 222b and meshes with the second inner ring gear 223b. The outer diameter of the third planetary gear 222b is larger than the outer diameter of the fourth planetary gear 225b.

[0160] The second planetary carrier 224b includes a second holder 2241b and a second rotation shaft 2242b. The second holder 2241b is provided on the opposite side of the third planetary gear 222b from the fourth planetary gear 225b. The second rotation shaft 2242b is parallel to the axis of the second sun gear 221b, and one end of the second rotation shaft 2242b is connected to the second holder 2241b. The second rotation shafts 2242b are the same in number as the third planetary gears 222b, and the second rotation shafts 2242b are provided in one-to-one correspondence with the third planetary gears 222b, and the second rotation shafts 2242b are provided in one-to-one correspondence with the fourth planetary gears 225b, and the third planetary gears 222b are fitted onto the corresponding second rotation shafts 2242b and can rotate about the second rotation shafts 2242b, and the fourth planetary gears 225b are fitted onto the corresponding second rotation shafts 2242b and can rotate about the second rotation shafts 2242b. The second driver shaft 23b is provided on the side of the second holder 2241b opposite the second sun gear 221b, and is provided so as to be coaxial with the second sun gear 221b. One end of the second driver shaft 23b is connected to the second holder 2241b of the second planetary carrier 224b.

[0161] The torque output from the main shaft of the second motor 21b is sent to the second driver shaft 23b via the second planetary gear mechanism 22b, thereby driving the second driver shaft 23b to rotate.

[0162] The first planetary gear mechanism 12a is a vertical double-row planetary gear mechanism, and the second planetary gear mechanism 22b is a horizontal double-row planetary gear mechanism, so the transmission ratios of the first planetary gear mechanism 12a and the second planetary gear mechanism 22b are both greater than the transmission ratio of a single-row planetary gear mechanism. Also, compared to the first planetary gear mechanism 12a configured as a vertical double-row planetary gear mechanism, the radial dimension of the second planetary gear mechanism 22b configured as a horizontal double-row planetary gear mechanism is smaller.

[0163] The first planetary gear mechanism 12a and the second planetary gear mechanism 22b are a vertical double-row planetary gear mechanism and a horizontal double-row planetary gear mechanism, respectively. Therefore, the gear arrangement methods of the first planetary gear mechanism 12a and the second planetary gear mechanism 22a are different, and torque is transmitted via different paths between them. This achieves order separation of the first planetary gear mechanism 12a and the second planetary gear mechanism 22b, and further prevents the orders of the first planetary gear mechanism 12a and the second planetary gear mechanism 22b from overlapping. This significantly reduces order noise when the first planetary gear mechanism 12a and the second planetary gear mechanism 22b operate simultaneously, improving the NVH performance of the vehicle and providing a more comfortable ride.

[0164] Additionally, the first motor 11a and the second motor 21b can be low-power motors. When the first motor 11a and the second motor 21b operate simultaneously, the dual-motor electric drive assembly 100i can output high power, meeting the high-power requirements of automobiles. Because the first motor 11a and the second motor 21b can be controlled independently, the power output of one or both motors can be changed according to power requirements, enabling functions such as differential, differential lock, and vector control for automobiles, resulting in more precise control. For example, by controlling the rotation speed and torque of the first motor 11a and the second motor 21a, respectively, differential speed and torque distribution between the wheels can be achieved, enabling the automobile to travel in a straight line.

[0165] In one exemplary embodiment, the number of teeth of the first sun gear 121a of the first planetary gear set 12a is different from the number of teeth of the second sun gear 221b of the second planetary gear set 22b.

[0166] The number of teeth of the first planetary gear 122a of the first planetary gear mechanism 12a is different from the number of teeth of both the third planetary gear 222b and the fourth planetary gear 225b of the second planetary gear mechanism 22b.

[0167] The number of teeth of the second planetary gear 125a of the first planetary gear mechanism 12a is different from the number of teeth of both the third planetary gear 222b and the fourth planetary gear 225b of the second planetary gear mechanism 22b.

[0168] In this way, the number of sun gear teeth and / or the number of planetary gear teeth are different between the first planetary gear mechanism 12a and the second planetary gear mechanism 22b, which further reduces harmonic noise when the first planetary gear mechanism 12a and the second planetary gear mechanism 22b operate simultaneously, improves the NVH performance of the automobile, and provides a more comfortable ride.

[0169] While this application has described several embodiments, this description is illustrative and not limiting, and those skilled in the art will recognize that additional embodiments and implementations are possible within the scope of the described embodiments. While many possible combinations of features are shown in the drawings and described in the detailed description, many other combinations of the disclosed features are possible. Any feature or element of any embodiment can be used with or substituted for any other feature or element of any other embodiment, unless otherwise specified.

[0170] The present application includes and contemplates combinations of features and elements known to those skilled in the art. The embodiments, features, and elements disclosed herein may also be combined with any conventional features or elements to form a unique inventive scheme defined by the claims. Any feature or element of any embodiment may also be combined with features or elements from other inventive solutions to form another unique inventive solution defined by the claims. Therefore, it should be understood that any of the features illustrated and / or described in this application may be practiced alone or in any suitable combination. Therefore, the embodiments are not limited by anything except as limited by the appended claims and their equivalents. Furthermore, various modifications and variations are possible within the scope of the appended claims.

[0171] Furthermore, in describing representative embodiments, the specification may present a method and / or process as a particular sequence of steps. However, unless the method or process relies on the particular order of steps described herein, the method or process should not be limited to the particular order of steps described. As will be understood by those skilled in the art, other orders of steps are possible. Thus, the particular order of steps described herein should not be construed as a limitation on the scope of the claims. Furthermore, claims directed to the method and / or process should not be limited to performing those steps in the order described; one skilled in the art can readily understand that these orders may be changed and still remain within the spirit and scope of the embodiments of the present application.

Claims

1. 1. A dual motor electric drive assembly comprising: a first drive mechanism and a second drive mechanism located on the same transaxle; the first drive mechanism includes a first motor, a first planetary gear mechanism, and a first driver shaft connected in sequence; the second drive mechanism includes a second motor, a second planetary gear mechanism, and a second driver shaft connected in sequence; wherein the first planetary gear mechanism and the second planetary gear mechanism are of different construction.

2. the gears of the first planetary gear mechanism and the gears of the second planetary gear mechanism are arranged symmetrically, 2. The dual motor electric drive assembly of claim 1, wherein the first motor and the second motor are connected to two gears whose positions are not symmetrical to each other in the first planetary gear set and the second planetary gear set, respectively.

3. 3. The dual motor electric drive assembly of claim 1, wherein an inner ring gear of the first planetary gear set is connected to a main shaft of the first motor and a sun gear of the second planetary gear set is connected to a main shaft of the second motor.

4. the first driver shaft and the second driver shaft are coaxial; The first planetary gear mechanism comprises: a first inner ring gear disposed coaxially with the first driver shaft and connected to a main shaft of the first motor; a first sun gear fixedly mounted within the first inner ring gear and coaxial with the first inner ring gear; a first planetary gear meshing with the first inner ring gear and the first sun gear; a first planetary carrier including a first holder fixedly connected to the first driver shaft and a first rotating shaft connected to the first holder, the first planetary gear being fitted onto the first rotating shaft; The second planetary gear mechanism is a second inner ring gear fixedly mounted coaxially with the second driver shaft; a second sun gear provided within the second inner ring gear, coaxial with the second inner ring gear, and fitted onto a main shaft of the second motor; a second planetary gear meshing with the second inner ring gear and the second sun gear; 2. The dual motor electric drive assembly of claim 1, further comprising: a second holder fixedly connected to the second driver shaft; and a second planet carrier including a second rotating shaft connected to the second holder, the second planet gears being fitted onto the second rotating shaft.

5. the first driver shaft and the second driver shaft are coaxial; The first planetary gear mechanism comprises: a first inner ring gear disposed coaxially with the first driver shaft and connected to a main shaft of the first motor; a first sun gear fixedly mounted within the first inner ring gear and coaxial with the first inner ring gear; a first planetary gear provided between the first sun gear and the first inner ring gear and meshing with the first sun gear; a second planetary gear provided between the first sun gear and the first inner ring gear and meshing with the first inner ring gear and the first planetary gear; a first planet carrier including a first holder fixedly connected to the first driver shaft and a first rotation shaft and a second rotation shaft both connected to the first holder, the first planet gear and the second planet gear being fitted onto the first rotation shaft and the second rotation shaft, respectively; The second planetary gear mechanism is a second inner ring gear fixedly mounted coaxially with the second driver shaft; a second sun gear provided within the second inner ring gear, coaxial with the second inner ring gear, and fitted onto a main shaft of the second motor; a third planetary gear provided between the second sun gear and the second inner ring gear and meshing with the second sun gear; a fourth planetary gear provided between the second sun gear and the second inner ring gear and meshing with the second inner ring gear and the third planetary gear; 2. The dual motor electric drive assembly of claim 1, including a second holder fixedly connected to the second driver shaft and a second planet carrier including third and fourth rotational shafts both connected to the second holder, the third and fourth planetary gears fitted onto the third and fourth rotational shafts, respectively.

6. the first driver shaft and the second driver shaft are coaxial; The first planetary gear mechanism comprises: a first sun gear fitted onto the main shaft of the first motor and provided coaxially with the first driver shaft; a first inner ring gear provided on a side of the first sun gear closer to the first motor and fixedly provided; a first planetary gear that meshes with the first sun gear; a second planetary gear meshing with the first inner ring gear; a first planet carrier including a first holder fixedly connected to the first driver shaft and a first rotating shaft connected to the first holder, the first planetary gear and the second planetary gear being fitted onto the first rotating shaft; The second planetary gear mechanism is a second inner ring gear disposed coaxially with the second driver shaft and connected to the second motor; a second sun gear fixedly provided on a side of the second inner ring gear opposite to the second motor and coaxial with the second inner ring gear; a third planetary gear that meshes with the second sun gear; a fourth planetary gear meshing with the second inner ring gear; 2. The dual motor electric drive assembly of claim 1, further comprising: a second holder fixedly connected to the second driver shaft; and a second planet carrier including a second rotating shaft connected to the second holder, the third planet gear and the fourth planet gear being fitted onto the second rotating shaft.

7. the first driver shaft and the second driver shaft are coaxial; The first planetary gear mechanism comprises: a first sun gear fitted onto the main shaft of the first motor and provided coaxially with the first driver shaft; a second sun gear fixedly provided on the opposite side of the first sun gear from the first motor and coaxial with the first sun gear; a first planetary gear that meshes with the first sun gear; a second planetary gear that meshes with the second sun gear; a first planet carrier including a first holder fixedly connected to the first driver shaft and a first rotating shaft connected to the first holder, the first planetary gear and the second planetary gear being fitted onto the first rotating shaft; The second planetary gear mechanism is a third sun gear that is coaxial with and fixed to the second driver shaft, that has a through hole through which a main shaft of the second motor passes, and that is clearance-fitted with the main shaft of the second motor; a fourth sun gear fitted onto a main shaft of the second motor and provided on the opposite side of the third sun gear from the second motor; a third planetary gear that meshes with the third sun gear; a fourth planetary gear that meshes with the fourth sun gear; 2. The dual motor electric drive assembly of claim 1, further comprising: a second holder fixedly connected to the second driver shaft; and a second planet carrier including a second rotating shaft connected to the second holder, the third planet gear and the fourth planet gear both fitted onto the second rotating shaft.

8. a plurality of the first planetary gears, the second planetary gears, the third planetary gears, the fourth planetary gears, the first rotation shafts, and the second rotation shafts are all provided; the first planetary gears are uniformly distributed in the circumferential direction of the first sun gear, the second planetary gear and the first planetary gear are provided in one-to-one correspondence, and the second planetary gear and the corresponding first planetary gear are fitted onto the same first rotation shaft, the third planetary gears are uniformly distributed in the circumferential direction of the second sun gear, 8. The dual motor electric drive assembly of claim 6 or 7, wherein the fourth planetary gear and the third planetary gear are provided in one-to-one correspondence, and the fourth planetary gear and the corresponding third planetary gear are fitted on the same second rotation shaft.

9. 8. The dual motor electric drive assembly of claim 6 or 7, wherein the first driver shaft, the first planetary gear set, the first motor, the second motor, the second planetary gear set, and the second driver shaft are arranged in sequence and coaxially.

10. 1. A dual motor electric drive assembly comprising: a first drive mechanism and a second drive mechanism; the first drive mechanism includes a first motor, a first gear transmission, and a first driver shaft, which are rotatably connected in sequence; the second drive mechanism includes a second motor, a second gear transmission, and a second driver shaft, which are rotatably connected in sequence; wherein the gears of the first gear transmission mechanism and the gears of the second gear transmission mechanism are arranged symmetrically, and at least two of the gears arranged symmetrically to each other have different numbers of teeth.

11. 11. The dual motor electric drive assembly according to claim 10, wherein the gears arranged symmetrically to each other in the first gear transmission mechanism and the second gear transmission mechanism all have different numbers of teeth.

12. 12. The dual motor electric drive assembly of claim 10 or 11, wherein the first gear transmission and the second gear transmission are all planetary gear transmissions.

13. 13. The dual motor electric drive assembly of claim 12, wherein the first gear transmission and the second gear transmission are all single-row planetary gear sets, horizontal double-row planetary gear sets, or vertical double-row planetary gear sets.

14. the first driver shaft and the second driver shaft are coaxial; The first gear transmission mechanism includes: a first inner ring gear fixedly mounted coaxially with the first driver shaft; a first sun gear provided within the first inner ring gear, coaxial with the first inner ring gear, and fitted onto a main shaft of the first motor; a first planetary gear meshing with the first inner ring gear and the first sun gear; a first planetary carrier including a first holder fixedly connected to the first driver shaft and a first rotating shaft connected to the first holder, the first planetary gear being fitted onto the first rotating shaft; The second gear transmission mechanism is a second inner ring gear fixedly mounted coaxially with the second driver shaft; a second sun gear provided within the second inner ring gear, coaxial with the second inner ring gear, and fitted onto a main shaft of the second motor; a second planetary gear meshing with the second inner ring gear and the second sun gear; a second planetary carrier including a second holder fixedly connected to the second driver shaft and a second rotating shaft connected to the second holder, the second planetary gears being fitted onto the second rotating shaft; 12. The dual motor electric drive assembly of claim 10 or 11, wherein the first inner ring gear and the second inner ring gear are symmetrically arranged, the first sun gear and the second sun gear are symmetrically arranged, and the first planetary gear and the second planetary gear are symmetrically arranged.

15. the first driver shaft and the second driver shaft are coaxial; The first gear transmission mechanism includes: a first inner ring gear fixedly mounted coaxially with the first driver shaft; a first sun gear provided within the first inner ring gear, coaxial with the first inner ring gear, and fitted onto a main shaft of the first motor; a first planetary gear provided between the first sun gear and the first inner ring gear and meshing with the first sun gear; a second planetary gear provided between the first sun gear and the first inner ring gear and meshing with the first inner ring gear and the first planetary gear; a first planet carrier including a first holder fixedly connected to the first driver shaft and a first rotation shaft and a second rotation shaft both connected to the first holder, the first planet gear and the second planet gear being fitted onto the first rotation shaft and the second rotation shaft, respectively; The second gear transmission mechanism is a second inner ring gear fixedly mounted coaxially with the second driver shaft; a second sun gear provided within the second inner ring gear, coaxial with the second inner ring gear, and fitted onto a main shaft of the second motor; a third planetary gear provided between the second sun gear and the second inner ring gear and meshing with the second sun gear; a fourth planetary gear provided between the second sun gear and the second inner ring gear and meshing with the second inner ring gear and the third planetary gear; a second planet carrier including a second holder fixedly connected to the second driver shaft and a third rotation shaft and a fourth rotation shaft both connected to the second holder, the third planet gear and the fourth planet gear being fitted onto the third rotation shaft and the fourth rotation shaft, respectively; 12. The dual motor electric drive assembly of claim 10 or 11, wherein the first inner ring gear and the second inner ring gear are symmetrically arranged, the first sun gear and the second sun gear are symmetrically arranged, the first planetary gear and the third planetary gear are symmetrically arranged, and the second planetary gear and the fourth planetary gear are symmetrically arranged.

16. the first driver shaft and the second driver shaft are coaxial; The first gear transmission mechanism includes: a first sun gear fitted onto the main shaft of the first motor and provided coaxially with the first driver shaft; a first inner ring gear provided on the opposite side of the first sun gear from the first motor and fixedly provided; a first planetary gear that meshes with the first sun gear; a second planetary gear meshing with the first inner ring gear; a first planet carrier including a first holder fixedly connected to the first driver shaft and a first rotating shaft connected to the first holder, the first planetary gear and the second planetary gear being fitted onto the first rotating shaft; The second gear transmission mechanism is a second sun gear fitted onto the main shaft of the second motor and coaxial with the second driver shaft; a second inner ring gear provided on the opposite side of the second sun gear from the second motor and fixedly provided; a third planetary gear that meshes with the second sun gear; a fourth planetary gear meshing with the second inner ring gear; a second planet carrier including a second holder fixedly connected to the second driver shaft and a second rotating shaft connected to the second holder, the third planetary gear and the fourth planetary gear being fitted onto the second rotating shaft; 12. The dual motor electric drive assembly of claim 10 or 11, wherein the first inner ring gear and the second inner ring gear are symmetrically arranged, the first sun gear and the second sun gear are symmetrically arranged, the first planetary gear and the third planetary gear are symmetrically arranged, and the second planetary gear and the fourth planetary gear are symmetrically arranged.

17. 17. The dual motor electric drive assembly of claim 16, wherein an outer diameter of the first planet gear is larger than an outer diameter of the second planet gear, and an outer diameter of the third planet gear is larger than an outer diameter of the fourth planet gear.

18. the first driver shaft and the second driver shaft are coaxial; The first gear transmission mechanism includes: a first sun gear fitted onto the main shaft of the first motor and provided coaxially with the first driver shaft; a second sun gear provided on the opposite side of the first sun gear from the first motor, coaxial with the first sun gear, and fixedly provided; a first planetary gear that meshes with the first sun gear; a second planetary gear that meshes with the second sun gear; a first planet carrier including a first holder fixedly connected to the first driver shaft and a first rotating shaft connected to the first holder, the first planetary gear and the second planetary gear being fitted onto the first rotating shaft; The second gear transmission mechanism is a third sun gear fitted onto the main shaft of the second motor and coaxial with the second driver shaft; a fourth sun gear provided on the opposite side of the third sun gear from the second motor, coaxial with the third sun gear, and fixedly provided; a third planetary gear that meshes with the third sun gear; a fourth planetary gear that meshes with the fourth sun gear; a second planet carrier including a second holder fixedly connected to the second driver shaft and a second rotating shaft connected to the second holder, wherein the third planetary gear and the fourth planetary gear are both fitted onto the second rotating shaft; 12. The dual motor electric drive assembly of claim 10 or 11, wherein the first sun gear and the third sun gear are symmetrically arranged, the second sun gear and the fourth sun gear are symmetrically arranged, the first planetary gear and the third planetary gear are symmetrically arranged, and the second planetary gear and the fourth planetary gear are symmetrically arranged.

19. 20. The dual motor electric drive assembly of claim 18, wherein an outer diameter of the first planet gear is larger than an outer diameter of the second planet gear, and an outer diameter of the third planet gear is larger than an outer diameter of the fourth planet gear.

20. 1. A dual motor electric drive assembly comprising: a first drive mechanism and a second drive mechanism located on the same transaxle; the first drive mechanism includes a first motor, a first planetary gear mechanism, and a first driver shaft connected in sequence; the second drive mechanism includes a second motor, a second planetary gear mechanism, and a second driver shaft connected in sequence; 1. A dual motor electric drive assembly, wherein the gears of the first planetary gear set and the second planetary gear set are arranged differently.

21. 21. The dual motor electric drive assembly of claim 20, wherein the first planetary gear set and the second planetary gear set are of different types.

22. 22. The dual motor electric drive assembly of claim 21, wherein said first planetary gear set is a single-row planetary gear set and said second planetary gear set is a double-row planetary gear set.

23. 22. The dual motor electric drive assembly of claim 21, wherein said first planetary gear set is a vertical double row planetary gear set and said second planetary gear set is a horizontal double row planetary gear set.

24. the number of teeth of the sun gear of the first planetary gear mechanism is different from the number of teeth of the sun gear of the second planetary gear mechanism; and / or 22. The dual motor electric drive assembly of claim 21, wherein the number of teeth on the planet gears of the first planetary gear set is different from the number of teeth on the planet gears of the second planetary gear set.

25. A motor vehicle, A motor vehicle comprising a dual motor electric drive assembly according to any one of claims 1 to 24.

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