Double-planet-row electric drive system and vehicle

Abstract

The invention belongs to the technical field of automobiles, and particularly relates to a double-planet-row electric drive system and a vehicle. The double-planet-row electric drive system comprises a first motor, a first planet row, a second motor and a second planet row. According to the double-planet-row electric drive system, speed reduction is achieved through the first planet row and the second planet row, the speed change effect is achieved through cooperation of the planet carriers and the sun gears in the first planet row and the second planet row, and therefore a traditional two-stage speed reduction scheme does not need to be adopted, and space occupation in the X-axis direction and the Z-axis direction is reduced; meanwhile, the number of bearings arranged in the gear is also reduced due to the fact that the transmission path is simplified through the double-planet-row structure, the requirement for bearing supporting points is lowered, and therefore reduction of transmission efficiency in an existing scheme can be avoided; besides, the output end of the first planet row is connected with the first wheel, the output end of the second planet row is connected with the second wheel, and therefore independent control and accurate power distribution of the two wheels are achieved.

Description

Technical Field

[0001] The present application belongs to the field of automotive technology, and specifically relates to a dual planetary gear electric drive system and a vehicle. Background Art

[0002] Existing distributed dual-motor drive systems usually adopt a parallel-axis T-type architecture and achieve power transmission through a two-stage parallel-axis transmission. This layout takes up a large space in the X-axis and Z-axis directions, affecting the layout design of the compact body. At the same time, the bearing mounting support requirements of multiple gears increase, which in turn leads to increased friction and mechanical losses in the transmission system, thereby reducing the overall transmission efficiency. In addition, the existing dual planetary gear drive solution usually adopts an embedded planetary gear structure, embedding two sets of planetary gears in the design and connecting the output end to one of the wheels. This solution limits the independent control ability of the wheels, which in turn affects the drive system's accurate regulation of wheel power distribution. Summary of the invention

[0003] One of the invention purposes of the present application is to provide a dual planetary gear electric drive system, which can not only optimize the space occupied in the X-axis and Z-axis directions in the vehicle layout, but also achieve independent and precise control of each wheel while ensuring transmission efficiency.

[0004] Another invention object of the present application is to provide a vehicle, wherein the vehicle includes the above-mentioned dual planetary gear electric drive system.

[0005] According to an embodiment of the present application, a first aspect provides a dual planetary gear electric drive system, comprising:

[0006] First motor;

[0007] A first planetary gear, wherein an input end of the first planetary gear is connected to the first motor, and an output end of the first planetary gear is connected to a first wheel;

[0008] a second motor, the second motor being arranged symmetrically with the first motor;

[0009] A second planetary row, wherein the second planetary row is symmetrically arranged with the first planetary row, an input end of the second planetary row is connected to the second motor, and an output end of the second planetary row is connected to the second wheel.

[0010] In one embodiment, the first planetary gear comprises a first sun gear, a plurality of first planetary gears, a first planet carrier and a first ring gear;

[0011] The input end of the first sun gear is connected to the first motor, a plurality of the first planetary gears are arranged between the first sun gear and the first ring gear and mesh with the first sun gear and the first ring gear, the first planetary carrier is connected to a plurality of the first planetary gears, and an output end of the first planetary carrier is connected to the first wheel.

[0012] In one embodiment, the first planetary gear comprises a first sun gear, a plurality of first planetary gears, a second sun gear, a plurality of second planetary gears, a first planet carrier, and a second planet carrier;

[0013] An input end of the first sun gear is connected to the first motor, and a plurality of the first planetary gears are meshed with the first sun gear;

[0014] The second sun gear has inner teeth and outer teeth, the second sun gear is arranged between the first planet gears and the second planet gears, the inner teeth of the second sun gear mesh with the first planet gears, and the outer teeth of the second sun gear mesh with the second planet gears;

[0015] The first planet carrier supports a plurality of the first planetary gears, and the first planet carrier is fixedly arranged;

[0016] The second planet carrier supports a plurality of the second planetary wheels, and an output end of the second planet carrier is connected to the first wheel.

[0017] In one embodiment, the composition of the second planetary gear is the same as that of the first planetary gear.

[0018] In one embodiment, the first ring gear in the second planetary gear set is integrated with the first ring gear of the first planetary gear set.

[0019] In one embodiment, the number of the first planetary gears is an even number greater than 2.

[0020] In one embodiment, the number of the first planetary gears and the number of the second planetary gears are both even numbers greater than 2.

[0021] In one embodiment, the dual planetary gear electric drive system further includes a ball bearing, and the ball bearing is used to support a transmission shaft connected to the first planetary gear and a transmission shaft connected to the second planetary gear.

[0022] In one embodiment, a transmission shaft connected to the first planetary gear unit passes through a central axis of the first motor, and a transmission shaft connected to the second planetary gear unit passes through a central axis of the second motor.

[0023] According to an embodiment of the present application, a second aspect provides a vehicle, comprising the dual planetary gear electric drive system.

[0024] The dual planetary gear electric drive system of the present application realizes deceleration through the first planetary gear and the second planetary gear. Since the speed change effect is realized by the cooperation between the planet carrier and the sun gear in the first planetary gear and the second planetary gear, there is no need to adopt the traditional two-stage deceleration scheme, thereby reducing the space occupied in the X-axis and Z-axis directions; at the same time, the number of bearings set in the gear is also reduced, because the dual planetary gear structure simplifies the transmission path and reduces the demand for bearing support points, thereby avoiding the reduction of transmission efficiency in the existing scheme; in addition, in the present application, the output end of the first planetary gear is connected to the first wheel, and the output end of the second planetary gear is connected to the second wheel, thereby realizing independent control of the two wheels and precise power distribution. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 This is a schematic diagram of the transmission structure of a double planetary gear electric drive system in one embodiment of the present application;

[0026] Figure 2 This is a schematic diagram of the transmission structure of a double planetary gear electric drive system in another embodiment of the present application;

[0027] Figure 3 This is a schematic diagram of the transmission structure of a double planetary gear electric drive system in another embodiment of the present application;

[0028] Figure 4 This is a schematic diagram of the transmission structure of a dual planetary gear electric drive system in another embodiment of the present application.

[0029] Description of Figure Numbers:

[0030] 110, first motor; 120, first wheel; 130, second motor; 140, second wheel;

[0031] 200, first planetary gear; 210, first sun gear; 220, first planetary gear;

[0032] 230, first planet carrier; 240, first ring gear; 250, second sun gear;

[0033] 260, second planetary gear; 270, second planetary carrier;

[0034] 300, second planetary gear;

[0035] 400. Drive shaft. DETAILED DESCRIPTION

[0036] In order to make the purpose, technical solution and advantages of the present application more clearly understood, the present application is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0037] It should be noted that the illustrations provided in this embodiment are only used to schematically illustrate the basic concept of the present invention.

[0038] The structures, proportions, sizes, etc. illustrated in the drawings in this specification are only used to match the contents disclosed in the specification so as to facilitate understanding and reading by persons familiar with this technology, and are not used to limit the conditions under which the present invention can be implemented. Any structural modification, change in proportion or adjustment of size should still fall within the scope of the technical contents disclosed in the present invention without affecting the effects and purposes that can be achieved by the present invention.

[0039] The directions or positional relationships indicated by the terms "upper", "lower", "left", "right", "middle", "longitudinal", "lateral", "horizontal", "inner", "outer", "radial", "circumferential" and the like in this specification are based on the directions or positional relationships shown in the drawings and are only for the convenience of simplifying the description. They do not indicate or imply that the devices or elements referred to must have a specific direction, be constructed and operate in a specific direction, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance.

[0040] As described in the background, the existing distributed dual-motor drive system usually adopts a parallel shaft T-type architecture and realizes power transmission through a two-stage parallel shaft transmission. This layout occupies a large space in the X-axis and Z-axis directions, affecting the layout design of the compact body. At the same time, the bearing installation support requirements of multiple gears increase, which in turn leads to increased friction and mechanical losses in the transmission system, thereby reducing the overall transmission efficiency. In addition, the existing dual planetary gear drive solution usually adopts an embedded planetary gear structure, embeds two sets of planetary gears in the design, and connects the output end to one of the wheels. This solution limits the independent control ability of the wheels, thereby affecting the accurate regulation of the drive system on the power distribution of the wheels. In order to better solve this problem, the researchers in this application proposed a dual planetary gear electric drive system, which can not only optimize the space occupancy in the X-axis and Z-axis directions in the vehicle layout, but also achieve independent and precise control of each wheel while ensuring transmission efficiency.

[0041] like Figure 1 As shown, Figure 1The schematic diagram of the transmission structure of the double planetary gear electric drive system in an embodiment of the present application. The double planetary gear electric drive system includes: a first motor 110, a first planetary gear 200, a second motor 130 and a second planetary gear 300. Among them, the power of the first motor 110 is input to the first planetary gear 200, and the first planetary gear 200 transmits and distributes the input power, and transmits the output power to the first wheel 120. The second motor 130 is symmetrically arranged and connected to the second planetary gear 300. Its power is input to the second planetary gear 300, and after transmission and distribution, it is output to the second wheel 140. The system realizes independent transmission and distribution of power through the double planetary gear structure. Compared with the traditional parallel axis T-type structure, it reduces the space occupied in the X-axis and Z-axis directions, and improves the layout flexibility of the compact body. At the same time, this solution reduces the bearing installation support requirements, reduces mechanical friction losses, and improves transmission efficiency. In addition, the double planetary gear independently connects the left and right wheels, which improves the independent regulation ability of wheel power distribution.

[0042] Specifically, the input end of the first planetary row 200 is connected to the first motor 110, and the output end of the first planetary row 200 is connected to the first wheel 120; the second motor 130 is symmetrically arranged with the first motor 110; the second planetary row 300 is symmetrically arranged with the first planetary row 200, the input end of the second planetary row 300 is connected to the second motor 130, and the output end of the second planetary row 300 is connected to the second wheel 140.

[0043] In this embodiment, the power of the first motor 110 is transmitted to the first planetary gear 200, and the first planetary gear 200 transmits the power to the first wheel 120; the power of the second motor 130 is transmitted to the second planetary gear 300, and the second planetary gear 300 transmits the power to the second wheel 140. The dual planetary gear electric drive system adopts the symmetrically arranged first motor 110 and second motor 130 and the symmetrical first planetary gear 200 and second planetary gear 300, transmits the power to the first wheel 120 through the first planetary gear 200, and transmits the power to the second wheel 140 through the second planetary gear 300, thereby realizing independent driving of the first wheel 120 and the second wheel 140.

[0044] Compared with the traditional distributed dual-motor drive system that adopts a parallel shaft T-type architecture and realizes power transmission through two-stage parallel shaft transmission, occupies a large space in the X-axis and Z-axis directions, and requires multiple gear bearing installation supports, which increases friction and mechanical losses, the dual planetary gear electric drive system in this embodiment simplifies the transmission path and reduces the transmission links through the direct connection between the first motor 110 and the first planetary gear 200 and the second motor 130 and the second planetary gear 300, thereby reducing the friction loss of the transmission system and improving the transmission efficiency.

[0045] At the same time, the dual planetary gear electric drive system in this embodiment realizes independent control of the wheels. When the vehicle needs to travel in a straight line, the first motor 110 and the second motor 130 are controlled to maintain the same speed, and the first wheel 120 and the second wheel 140 are driven to rotate synchronously to ensure that the vehicle travels in a straight line. When the vehicle needs to turn, the first motor 110 and the second motor 130 are controlled to run at different speeds, and the first wheel 120 and the second wheel 140 are driven to rotate at different speeds, so that the vehicle can turn according to different turning radii. When a wheel of the vehicle loses adhesion, torque is provided to the motor corresponding to the wheel that maintains adhesion to ensure that the vehicle successfully escapes.

[0046] In one embodiment, see Figure 1 As shown, the first planetary gear 200 includes a first sun gear 210, a plurality of first planetary gears 220, a first planetary carrier 230 and a first ring gear 240; the input end of the first sun gear 210 is connected to the first motor 110, the plurality of first planetary gears 220 are arranged between the first sun gear 210 and the first ring gear 240, and are meshed with the first sun gear 210 and the first ring gear 240, the first planetary carrier 230 is connected to the plurality of first planetary gears 220, and the output end of the first planetary carrier 230 is connected to the first wheel 120.

[0047] In this embodiment, the power of the first motor 110 is input into the transmission system of the first planetary gear 200 through the first sun gear 210. The first sun gear 210 drives the plurality of first planetary gears 220 to rotate around the first sun gear 210. The first planetary gears 220 mesh with the first ring gear 240, and drive the first planetary carrier 230 to rotate during the rotation of the first planetary gear 220. The rotational power of the first planetary carrier 230 is transmitted to the first wheel 120 through the output end. In the structure of the first planetary gear 200, the first sun gear 210 is connected to the first motor 110, and the plurality of first planetary gears 220 are arranged between the first sun gear 210 and the first ring gear 240 to form a meshing transmission path. The first planetary carrier 230 is connected to the plurality of first planetary gears 220 and is connected to the first wheel 120 through the output end, forming a single-stage reduction transmission chain from the motor to the wheel. In this embodiment, the first planetary gear 200 converts the high speed and low torque characteristics of the first motor 110 into the low speed and high torque characteristics required by the first wheel 120, meeting the vehicle driving requirements. It should be noted that the composition of the second planetary gear set 300 may be the same as the composition of the first planetary gear set 200 .

[0048] In another embodiment, see Figure 2As shown, the first planetary gear 200 includes a first sun gear 210, a plurality of first planetary gears 220, a second sun gear 250, a plurality of second planetary gears 260, a first planet carrier 230 and a second planet carrier 270; the input end of the first sun gear 210 is connected to the first motor 110, and the plurality of first planetary gears 220 are meshed with the first sun gear 210; the second sun gear 250 has inner teeth and outer teeth, and the second sun gear 250 is arranged between the plurality of first planetary gears 220 and the plurality of second planetary gears 260, the inner teeth of the second sun gear 250 are meshed with the plurality of first planetary gears 220, and the outer teeth of the second sun gear 250 are meshed with the plurality of second planetary gears 260; the first planet carrier 230 supports the plurality of first planetary gears 220, and the first planet carrier 230 is fixedly arranged; the second planet carrier 270 supports the plurality of second planetary gears 260, and the output end of the second planet carrier 270 is connected to the first wheel 120.

[0049] In this embodiment, a compound planetary gear structure is adopted, the first motor 110 drives the first sun gear 210, and the first sun gear 210 drives the plurality of first planetary gears 220 to rotate. Since the first planetary carrier 230 is fixed, the first planetary gear 220 rotates around itself and drives the second sun gear 250 to rotate through the internal teeth meshing between the first planetary gear 220 and the second sun gear 250. The second sun gear 250 drives the plurality of second planetary gears 260 through the external teeth, and the second planetary gears 260 drive the second planetary carrier 270 to rotate, and the second planetary carrier 270 transmits power to the first wheel 120.

[0050] The reduction ratio of the transmission system is increased by the design of multiple first planetary gears 220 and multiple second planetary gears 260. Specifically, the fixed first planetary carrier 230 causes the first planetary gear 220 to rotate and drive the second sun gear 250 to rotate, completing the first stage of reduction; the second sun gear 250 drives the second planetary gear 260 to drive the second planetary carrier 270 to rotate, completing the second stage of reduction. The series combination of the two-stage reduction process makes the reduction ratio obtained at the output end the product of the two-stage reduction ratios, significantly improving the total reduction ratio. The increase in the reduction ratio is converted into a higher torque output capacity at the output end, meeting the vehicle's torque requirements under various driving conditions. It should be noted that the composition of the second planetary gear 300 can be the same as that of the first planetary gear 200.

[0051] In one embodiment, the composition of the second planetary gear train 300 is the same as that of the first planetary gear train 200 .

[0052] In this embodiment, the second planetary gear 300 adopts the same composition structure as the first planetary gear 200, realizing the symmetrical design of the system. The symmetrical structural design enables the first planetary gear 200 and the second planetary gear 300 to have the same transmission characteristics and transmission efficiency, ensuring that the first wheel 120 and the second wheel 140 obtain consistent power output response. The symmetrical design increases the versatility of system components, facilitates system integration and assembly, and reduces system complexity. At the same time, the consistency of the structure helps to achieve a balanced distribution of the system load, avoid unilateral structural overload, and improve the reliability and durability of the transmission system.

[0053] In one embodiment, see Figure 3 and Figure 3 As shown, the first ring gear 240 in the second planetary gear set 300 is integrated with the first ring gear 240 of the first planetary gear set 200 .

[0054] In this embodiment, the first ring gear 240 in the second planetary gear set 300 is integrated with the first ring gear 240 of the first planetary gear set 200 , thereby reducing the number of first ring gears 240 used and also reducing the complexity of component assembly.

[0055] In one embodiment, the number of the first planetary gears 220 is an even number greater than 2.

[0056] In this embodiment, the number of the first planetary gears 220 is designed to be an even number greater than 2 to ensure that they are evenly distributed around the first sun gear 210. From the perspective of speed ratio, when the number of the first planetary gears 220 increases, under the condition of fixing the diameter of the first ring gear 240, in order to maintain the meshing relationship, the diameter of the first sun gear 210 will increase accordingly, while the diameter of the first planetary gear 220 will decrease. According to the calculation formula of the planetary gear transmission speed ratio, the transmission ratio is directly related to the gear ratio of the first sun gear 210 and the first ring gear 240. The increase in the diameter of the first sun gear 210 leads to an increase in its number of teeth, thereby changing the speed ratio coefficient, so that the planetary gear system can obtain a wider range of transmission ratio adjustment capabilities. This design enables the system to achieve more accurate power matching under different vehicle speeds and working conditions. The design of an even number of first planetary gears 220 is to ensure that the force of the first sun gear 210 is symmetrical, thereby forming a mechanical balance structure.

[0057] In another embodiment, the number of the first planetary gears 220 and the number of the second planetary gears 260 are both even numbers greater than two.

[0058] In this embodiment, the number of the first planetary gears 220 and the second planetary gears 260 are designed to be an even number greater than 2, which, on the one hand, enables the first planetary gear 200 to have a wider range of transmission ratio adjustment capabilities, and also makes the first sun gear 210 and the second sun gear 250 symmetrical in force.

[0059] In one embodiment, the dual planetary gear electric drive system further includes a ball bearing, and the ball bearing is used to support the transmission shaft 400 connected to the first planetary gear 200 and the transmission shaft 400 connected to the second planetary gear 300 .

[0060] In this embodiment, ball bearings are used to support the transmission shaft 400. Compared with tapered roller bearings, ball bearings have a lower friction coefficient, which can reduce the energy loss of the transmission system. The coaxial layout of the dual planetary gear electric drive system reduces the number of bearings, while the distributed dual electric drive system of the traditional parallel shaft T-type architecture requires multiple bearings to support each level of transmission gears, which increases the system complexity and friction loss. This embodiment uses a symmetrical structure to offset the axial forces of the gears, reduce bearing loads, and reduce mechanical losses, thereby improving transmission efficiency. The coaxial structure simplifies the transmission path, avoids the additional loss of power steering transmission in the T-type architecture, and achieves more efficient energy transmission.

[0061] In one embodiment, see Figure 1 and Figure 2 As shown, the transmission shaft 400 connected to the first planetary gear 200 passes through the central axis of the first motor 110 , and the transmission shaft 400 connected to the second planetary gear 300 passes through the central axis of the second motor 130 .

[0062] In this embodiment, the transmission shaft 400 connected to the first planetary gear 200 passes through the central axis of the first motor 110, and the transmission shaft 400 connected to the second planetary gear 300 passes through the central axis of the second motor 130, thereby improving the rigidity of the rotors of the first motor 110 and the second motor 130, reducing the warping deformation of the first motor 110 and the second motor 130 during high-speed operation, and increasing the upper limit of the speed of the first motor 110 and the second motor 130.

[0063] Taking the first motor 110 as an example, the transmission shaft 400 passes through the central axis of the first motor 110 to form a coaxial penetration structure, which provides additional support for the rotor of the first motor 110, so that the force of the rotor of the first motor 110 is more balanced. When the first motor 110 is in a high-speed operation state, the rotor of the first motor 110 may produce flexural deformation and vibration, especially when the speed of the first motor 110 is close to the critical speed, the amplitude of the rotor of the first motor 110 will increase significantly. The coaxial penetration structure of the transmission shaft 400 passing through the central axis of the first motor 110 provides more stable support at both ends of the rotor, so that the force state of the rotor of the first motor 110 is changed from single-end or cantilever support to double-point support, thereby improving the stiffness of the rotor system of the first motor 110. According to the natural frequency calculation formula, the increase in system stiffness will lead to an increase in natural frequency. Therefore, the solution in this embodiment can effectively improve the natural frequency of the first motor 110, so that the resonance point of the first motor 110 is far away from the conventional working speed range, improve the anti-resonance ability, and enable the first motor 110 to operate stably within a higher speed range.

[0064] The present application also proposes a vehicle, wherein the vehicle includes the above-mentioned dual planetary gear electric drive system.

[0065] In this embodiment, when the above-mentioned dual planetary gear electric drive system is installed in the vehicle, the compact layout and efficient transmission of the vehicle drive system are realized. The dual planetary gear electric drive system adopts a symmetrically arranged first motor 110 and a second motor 130, and a symmetrically arranged first planetary gear 200 and a second planetary gear 300, and adopts the first planetary gear 200 to control the first wheel 120, and adopts the second planetary gear 300 to control the second wheel 140, thereby overcoming the problem that the traditional parallel axis T-type structure occupies a large space in the X-axis and Z-axis directions, and adapting to the layout requirements of the compact vehicle body. At the same time, the dual planetary gear electric drive system reduces the number of transmission links and bearings, reduces the mechanical loss of the transmission system, and improves the transmission efficiency. In addition, the dual planetary gear electric drive system realizes independent control of the wheels, enhances the handling performance of the vehicle, and improves the adaptability of the vehicle under various road conditions.

[0066] The technical features of the above embodiments may be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0067] The above embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the invention patent. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent of the present application shall be subject to the attached claims.

Claims

1. A double planetary gear electric drive system, characterized in that: include: A first motor (110); A first planetary gear (200), wherein an input end of the first planetary gear (200) is connected to the first motor (110), and an output end of the first planetary gear (200) is connected to a first wheel (120); a second motor (130), the second motor (130) being arranged symmetrically with the first motor (110); A second planetary gear (300), wherein an input end of the second planetary gear (300) is connected to the second motor (130), and an output end of the second planetary gear (300) is connected to a second wheel (140).

2. The double planetary gear electric drive system according to claim 1, characterized in that: The first planetary gear (200) comprises a first sun gear (210), a plurality of first planetary gears (220), a first planet carrier (230) and a first ring gear (240); The input end of the first sun gear (210) is connected to the first motor (110), a plurality of the first planetary gears (220) are arranged between the first sun gear (210) and the first ring gear (240), and mesh with the first sun gear (210) and the first ring gear (240), the first planetary carrier (230) is connected to the plurality of the first planetary gears (220), and the output end of the first planetary carrier (230) is connected to the first wheel (120).

3. The double planetary gear electric drive system according to claim 1, characterized in that: The first planetary gear (200) comprises a first sun gear (210), a plurality of first planetary gears (220), a second sun gear (250), a plurality of second planetary gears (260), a first planet carrier (230) and a second planet carrier (270); The input end of the first sun gear (210) is connected to the first motor (110), and the plurality of first planetary gears (220) are meshed with the first sun gear (210); The second sun gear (250) has internal teeth and external teeth. The second sun gear (250) is arranged between the plurality of the first planetary gears (220) and the plurality of the second planetary gears (260). The internal teeth of the second sun gear (250) mesh with the plurality of the first planetary gears (220), and the external teeth of the second sun gear (250) mesh with the plurality of the second planetary gears (260). The first planet carrier (230) supports a plurality of the first planetary gears (220), and the first planet carrier (230) is fixedly arranged; The second planet carrier (270) supports a plurality of the second planetary wheels (260), and an output end of the second planet carrier (270) is connected to the first wheel (120).

4. The double planetary gear electric drive system according to claim 2 or 3, characterized in that: The composition of the second planetary gear (300) is the same as that of the first planetary gear (200).

5. The double planetary gear electric drive system according to claim 4, characterized in that: The first ring gear (240) in the second planetary gear set (300) is integrated with the first ring gear (240) of the first planetary gear set (200).

6. The double planetary gear electric drive system according to claim 2, characterized in that: The number of the first planetary gears (220) is an even number greater than 2.

7. The double planetary gear electric drive system according to claim 3, characterized in that: The number of the first planetary gears (220) and the number of the second planetary gears (260) are both even numbers greater than 2.

8. The double planetary gear electric drive system according to claim 1, characterized in that: The dual planetary gear electric drive system further comprises a ball bearing, wherein the ball bearing is used to support a transmission shaft (400) connected to the first planetary gear (200) and a transmission shaft (400) connected to the second planetary gear (300).

9. The double planetary gear electric drive system according to claim 1, characterized in that: A transmission shaft (400) connected to the first planetary gear (200) passes through the central axis of the first motor (110), and a transmission shaft (400) connected to the second planetary gear (300) passes through the central axis of the second motor (130).

10. A vehicle, characterized in that: The vehicle comprises the dual planetary gear electric drive system according to any one of claims 1 to 9.

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