Distributed multi-gear driving system with central dual-motor opposed configuration and control method

Abstract

The invention discloses a distributed multi-gear driving system with double central motors oppositely arranged and a control method, and belongs to the technical field of mechanical driving transmission, the distributed multi-gear driving system comprises two driving systems used for driving wheels, and the two driving systems are oppositely arranged in a mirror image mode with the driving axes of the driving systems as the center; and the two driving systems respectively comprise a motor and a speed reducing mechanism which are coaxially arranged. The two driving systems which are oppositely arranged in a mirror image mode with the driving axis as the center are adopted, driving shafts are centered and symmetrically output, and eccentricity is reduced; the motor and the speed reducing mechanism are coaxially arranged to save space; planetary transmission and cylindrical gear compound transmission realize a large transmission ratio; three speed ratios are conveniently switched through the compound gear mechanism and the gear shifting mechanism, and the performance of the motor is fully exerted; electronic differential is achieved by combining the eccentric design of the cylindrical gear assembly and motor control, and the efficient, smooth and multi-gear requirements of electric drive vehicle types under complex working conditions are met.

Description

Technical Field

[0001] This invention belongs to the field of mechanical drive and transmission technology, specifically, it relates to a distributed multi-gear drive system and control method with a central dual-motor opposed configuration. Background Technology

[0002] Currently, distributed drive technology is evolving from centralized drive towards greater flexibility and efficiency. Its core lies in enabling more precise dynamic control of the vehicle by independently configuring a drive motor for each wheel. However, existing distributed drive technologies, while pursuing high performance and flexible deployment, face a series of fundamental structural challenges. Existing dual-motor distributed drive systems generally adopt coaxial arrangement or parallel eccentric arrangement of two motors on the same side. However, coaxial arrangement is difficult to design due to high space requirements, while parallel arrangement is complex and costly due to severe center of gravity eccentricity. At the same time, electric drive systems mostly use cylindrical motors with large axial dimensions, which occupy a lot of space and have a large mass when arranged parallel to the drive shaft in distributed drive. In addition, the transmission system design is complex, with both planetary transmission schemes and cylindrical gear schemes. However, compound gear transmissions are mostly used in fuel vehicles or hybrid vehicles, and planetary gears are difficult to design and have a complex structure. Pure electric drive assemblies mostly use single-stage reducers, and the transmission ratio is limited, which prevents the motor from operating in the high-efficiency range for a long time. Although existing drive assemblies adopt eccentric design, they are mostly motor offset designs and integrated differentials, which still have the problems of severe center of gravity eccentricity and complex structure.

[0003] No effective solution to the above problems has yet been found. Summary of the Invention

[0004] The technical problem this invention addresses is the significant eccentricity of existing dual-motor distributed drive systems, which often employ a parallel offset arrangement; the use of axial cylindrical motors results in large space and mass; and the reduction mechanisms are mostly two-stage cylindrical gears or planetary gear structures, with the former having a small speed ratio range and the latter exhibiting complex structures when coaxially arranged. This invention provides a distributed multi-gear drive system and control method with a centrally opposed dual-motor configuration. By adopting a centrally opposed dual-motor drive system and combining a flat axial flux motor with a coaxial design for the reduction mechanism, the eccentric torque is effectively reduced and axial space is saved. A large transmission ratio is achieved through a composite transmission of planetary and cylindrical gears, and a three-speed ratio shifting function is integrated to adapt to the high-efficiency range of the motors. Electronic differential is achieved through the eccentric design of the gears and coordinated control with the motors, improving vehicle handling.

[0005] To solve the above technical problems, the technical solution adopted by the present invention is as follows: A distributed multi-speed drive system with a central dual-motor opposing configuration includes two drive systems for driving the wheels, the two drive systems being mirror-opposite to each other with the drive axis of the drive system as the center; The two drive systems each include a motor and a reduction gear mechanism arranged coaxially.

[0006] Preferably, the motor is a flat axial flux motor.

[0007] Preferably, the reduction mechanism includes a compound gear mechanism and a shifting mechanism; The compound gear mechanism includes a planetary transmission assembly and a cylindrical gear assembly. The planetary transmission assembly and the shifting mechanism are combined to achieve multiple gear switching.

[0008] Preferably, the planetary transmission assembly includes a P1 sun gear, a P1 planet gear, a P1 planet carrier, a P2 sun gear, a P2 planet gear, a P1 ring gear, a P2 planet carrier, a P2 ring gear, and a housing; The output shaft of the motor is connected to the P1 sun gear, the P1 planet gear is mounted on the P1 planet carrier, the P1 sun gear meshes externally with the P1 planet gear, and the P1 planet gear meshes internally with the P1 gear ring. The P1 planetary carrier and the P2 sun gear are coaxially connected. The P2 planet gear is mounted on the P2 planetary carrier. The P2 sun gear meshes externally with the P2 planet gear, and the P2 planet gear meshes internally with the P2 gear ring. The P2 gear ring is connected to the housing, and the P2 planetary carrier is connected to the cylindrical gear assembly for transmission.

[0009] Preferably, the shifting mechanism includes a C1 shifting device and a C2 shifting device, wherein the C1 shifting device is disposed on the P1 sun gear and the C2 shifting device is disposed on the P1 gear ring. The C1 shifting device is provided with a first synchronization ring, and the C2 shifting device is provided with a second synchronization ring.

[0010] Preferably, the cylindrical gear assembly includes a meshing driving gear and a driven gear; The driving wheel is coaxially connected to the P2 planetary carrier, the driven wheel is coaxially connected to an output shaft, and the output shaft is coaxially connected to the wheel.

[0011] The control method for the distributed multi-gear drive system with the central dual-motor opposed configuration includes: a first-gear switching step, controlling the second synchronous ring to move to the left and connect with the housing, the C2 shifting device locking the housing, the P1 planetary gear rotating and revolving around the P1 sun gear, the P1 sun gear driving the P1 planetary gear to rotate, the P1 planetary gear driving the P1 planetary carrier to rotate, the P1 planetary carrier driving the P2 sun gear to rotate, the P2 sun gear driving the P2 planetary gear to rotate, the P2 planetary gear driving the P2 planetary carrier to rotate, and outputting power at a reduced speed through the P2 planetary carrier.

[0012] Preferably, it further includes: a two-stage switching step, controlling the second synchronous ring to move to the right and connect with the P2 planetary carrier, the P1 sun gear drives the P1 planetary gear to rotate, the P1 planetary gear drives the P1 gear ring and the P1 planetary carrier to rotate; the P1 planetary carrier is connected to the P2 sun gear and rotates together, the P2 sun gear drives the P2 planetary gear to rotate, the P2 planetary gear drives the P2 planetary carrier to rotate, the P1 gear ring is connected to the P2 planetary carrier and rotates together, and power is transmitted through the P2 planetary carrier.

[0013] Preferably, it also includes: a 3-speed switching step, controlling the first synchronous ring to move to the right and connect with the P1 gear ring, the P1 gear ring and the P1 sun gear to form a component, the P2 sun gear driving the P2 planet gear to rotate, the P2 planet gear driving the P2 planet carrier to rotate to transmit power.

[0014] Preferably, it further includes: a neutral shifting step, in which the first synchronous ring is controlled to move to the left and be in a free state, the C1 shifting device locks the P1 sun gear, and the P1 planetary carrier and P1 ring gear are in a free state with no power transmission.

[0015] The present invention adopts the above technical solution and has the following advantages compared with the prior art: 1. The technical solution of the present invention uses two identical drive systems, which are mirror-oriented with the drive axis as the center. The output is in the middle position, driving the left and right wheels respectively, effectively utilizing space and reducing eccentricity.

[0016] 2. The technical solution of this invention uses a flat axial flux motor instead of a cylindrical motor, which can be arranged coaxially with the reduction mechanism, saving axial dimensions.

[0017] 3. The technical solution of this invention uses a composite gear transmission system of planetary transmission components and cylindrical gear components, which can achieve a large transmission ratio, has a simple structure, and low cost.

[0018] 4. The technical solution of this invention uses a compound gear mechanism and a shifting mechanism to achieve three speed ratios, and the shifting is simple, giving full play to the performance of the motor.

[0019] 5. The technical solution of this invention uses a cylindrical gear assembly to achieve eccentricity between the power input of the motor and the power output of the transmission system, and uses motor control to achieve electronic differential speed. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of the overall structure of the distributed multi-speed drive system with a central dual-motor opposing configuration in an embodiment of the present invention. Figure 2 This is a schematic diagram of the drive system for driving the right wheel in an embodiment of the present invention; Figure 3 This is a schematic diagram of the drive system for driving the left wheel in an embodiment of the present invention; Among them: 1-drive system, 2-motor, 3-output shaft, 4-drive gear, 5-driven gear, 6-P1 sun gear, 7-P1 planetary gear, 8-P1 planetary carrier, 9-P2 sun gear, 10-P2 planetary gear, 11-P1 gear ring, 12-P2 planetary carrier, 13-P2 gear ring, 14-C1 shifting device, 15-C2 shifting device, 16-housing; 101-Drive system, 201-Motor, 301-Output shaft, 401-Driving gear, 501-Driven gear, 601-P1 Sun gear, 701-P1 Planetary gear, 801-P1 Planetary carrier, 901-P2 Sun gear, 110-P2 Planetary gear, 111-P1 Gear ring, 121-P2 Planetary carrier, 131-P2 Gear ring, 141-C1 Shifting device, 151-C2 Shifting device, 161-Housing. Detailed Implementation

[0021] The present invention will be further described below. Those skilled in the art should understand through the following embodiments that these embodiments are not intended to limit the technical solution of the present invention, but merely to fully illustrate how to implement it.

[0022] Implementation examples, by Figure 1-3 As shown, the distributed multi-speed drive system with a central dual-motor opposing configuration includes two identical drive systems. The two drive systems are mirror-oriented with the drive axis of the drive system as the center. They are drive system 1 for driving the right wheel and drive system 101 for driving the left wheel. The output of the drive system is in the middle position, driving the left and right wheels respectively. This can effectively utilize space and reduce eccentricity.

[0023] The two drive systems have the same structure. This embodiment will take drive system 1 as an example for detailed description.

[0024] The drive system 1 includes a motor 2 and a reduction mechanism arranged coaxially. The output shaft of the motor 2 is aligned with the input shaft of the reduction mechanism, thereby saving axial space and making the structure more compact.

[0025] Motor 2 is a flat axial flux motor, replacing the cylindrical motor.

[0026] The speed reduction mechanism includes a compound gear mechanism and a shifting mechanism.

[0027] The compound gear mechanism includes a planetary transmission assembly and a cylindrical gear assembly; the planetary transmission assembly and the shifting mechanism are combined to achieve multiple gear switching.

[0028] The planetary transmission assembly includes a sun gear 6 (P1), planet gears 7 (P1), planet carrier 8 (P1), sun gear 9 (P2), planet gears 10 (P2), ring gear 11 (P1), planet carrier 12 (P2), ring gear 13 (P2), and housing 16.

[0029] The output shaft of motor 2 is connected to sun gear 6 of P1, and planet gear 7 of P1 is mounted on planet carrier 8 of P1. Planet carrier 8 of P1 is a rotating frame that supports planet gear 7 of P1 and transmits power. Sun gear 6 of P1 meshes externally with planet gear 7 of P1, and planet gear 7 of P1 meshes internally with ring gear 11 of P1.

[0030] Planet carrier 8 (P1) and sun gear 9 (P2) are coaxially connected. Planet gear 10 (P2) is mounted on planet carrier 12 (P2). Sun gear 9 and planet gear 10 are externally meshed, while planet gear 10 is internally meshed with ring gear 13 (P2). Planet carrier 12 (P2) is a rotating frame that supports planet gear 10 and transmits power. Ring gear 13 (P2) is connected to housing 16, and planet carrier 12 (P2) is connected to a cylindrical gear assembly for transmission.

[0031] The shifting mechanism can be a clutch or a synchronizer, and includes a C1 shifting device 14 and a C2 shifting device 15. The C1 shifting device 14 is mounted on the P1 sun gear 6, and the C2 shifting device 15 is mounted on the P1 gear ring 11.

[0032] The C1 shifting device 14 is provided with a first synchronous ring, and the C2 shifting device 15 is provided with a second synchronous ring. Both the first and second synchronous rings are existing technologies and are not shown in the figure. When the system shifts gears, the first and second synchronous rings can achieve speed synchronization through friction.

[0033] The cylindrical gear assembly includes a driving gear 4 and a driven gear 5. The driving gear 4 is coaxially connected to the P2 planetary carrier 12. The driving gear 4 meshes with the driven gear 5. The driven gear 5 is connected to an output shaft 3, which is coaxially connected to the wheel.

[0034] The cylindrical gear assembly is eccentrically positioned, with the driving gear 4 meshing with the driven gear 5. By adjusting the transmission ratio and relative position of the driving gear 4 and driven gear 5, the entire cylindrical gear assembly achieves an eccentric rotation effect, thereby driving the entire drive system to realize its eccentric design. Through the eccentric setting of the cylindrical gear assembly, combined with motor control, electronic differential can achieve precise power distribution to each wheel.

[0035] By adjusting the relevant parameters of the cylindrical gear assembly and the planetary transmission assembly, multiple transmission ratios of the drive system can be achieved. The transmission ratio in this embodiment is a preferred one.

[0036] The control method for a distributed multi-speed drive system with a central dual-motor opposed configuration that implements the above drive system includes: In the first gear shifting step, the second synchronous ring is controlled to move to the left and connect with the housing 16. The C2 shifting device 15 locks the housing 16, and the P1 gear ring 11 is fixed and cannot rotate. Power cannot be transmitted through the P1 gear ring 11. The P1 planetary gear 7 rotates on its own axis and revolves around the P1 sun gear 6. The P1 sun gear 6 drives the P1 planetary gear 7 to rotate. The P1 planetary gear 7 drives the P1 planet carrier 8 to rotate. The P1 planet carrier 8 drives the P2 sun gear 9 to rotate. The P2 sun gear 9 drives the P2 planetary gear 10 to rotate. The P2 planetary gear 10 drives the P2 planet carrier 12 to rotate. Power is output at a reduced speed through the P2 planet carrier 12.

[0037] The specific power transmission is as follows: motor 2 transmits power to P1 sun gear 6, P1 sun gear 6 transmits power to P1 planet gear 7, P1 planet gear 7 transmits power to P1 planet carrier 8, P1 planet carrier 8 transmits power to P2 sun gear 9, P2 sun gear 9 transmits power to P2 planet gear 10, P2 planet gear 10 transmits power to P2 planet carrier 12, P2 planet carrier 12 transmits power to drive gear 4, drive gear 4 transmits power to driven gear 5, and finally transmits power to the wheels through the output shaft 3, realizing the first gear shift with a transmission ratio of 26.4.

[0038] In the second gear switching step, the second synchronous ring is controlled to move to the right and connect with the P2 planetary carrier 12. The P1 gear ring 11 is no longer fixed. The P1 gear ring 11 and the P2 planetary carrier 12 are connected to form a single component. The P1 planetary gear 7 is no longer fixed. The P1 sun gear 6 drives the P1 planetary gear 7 to rotate. The P1 planetary gear 7 drives the P1 gear ring 11 and the P1 planetary carrier 8 to rotate. The P1 planetary carrier 8 is connected to the P2 sun gear 9 and rotates together. The P2 sun gear 9 drives the P2 planetary gear 10 to rotate. The P2 planetary gear 10 drives the P2 planetary carrier 12 to rotate. The P1 gear ring 11 is connected to the P2 planetary carrier 12 and rotates together, transmitting power through the P2 planetary carrier 12.

[0039] The specific power transmission is as follows: Motor 2 transmits power to P1 sun gear 6, P1 sun gear 6 transmits power to P1 planet gear 7, P1 planet gear 7 transmits power to P1 planet carrier 8 and P1 ring gear 11. Because C2 shifting device 15 is locked to P2 planet carrier 12, P1 planet carrier 8 transmits power to P2 sun gear 9, P2 sun gear 9 transmits power to P2 planet gear 10, P2 planet gear 10 transmits power to P2 planet carrier 12, P1 ring gear 11 and P2 planet carrier 12 rotate synchronously, P1 ring gear 11 transmits power to P2 planet carrier 12, P2 planet carrier 12 transmits power to drive gear 4, drive gear 4 transmits power to driven gear 5, and finally the power is transmitted to the wheels through output shaft 3, realizing 2-speed switching with a transmission ratio of 19.6.

[0040] In the three-speed switching steps, the first synchronous ring is controlled to move to the right and connect with the P1 gear ring 11. The P1 gear ring 11 and the P1 sun gear 6 are connected to form a component. The P1 planet gear 7 only revolves around the sun and does not rotate on its own axis, so there is no speed change, forming a direct transmission. The P1 sun gear 6, the P1 planet carrier 8 and the P1 gear ring 11 rotate as a whole. The P1 planet carrier 8 drives the P2 sun gear 9 to rotate, the P2 sun gear 9 drives the P2 planet gear 10 to rotate, and the P2 planet gear 10 drives the P2 planet carrier 12 to rotate to transmit power.

[0041] The specific power transmission is as follows: motor 2 transmits power to P1 sun gear 6, P1 sun gear 6 transmits power to P1 planet gear 7, P1 ring gear 11 and P1 planet carrier 8, P1 planet carrier 8 transmits power to P2 sun gear 9, P2 sun gear 9 transmits power to P2 planet gear 10, P2 planet gear 10 transmits power to P2 planet carrier 12, P2 planet carrier 12 transmits power to drive gear 4, drive gear 4 transmits power to driven gear 5, and finally output shaft 3 transmits power to the wheels, realizing 3-speed switching with a transmission ratio of 8.8.

[0042] In the neutral shifting step, the first synchronous ring is controlled to move to the left and is in a free state. The C1 shifting device 14 locks the P1 sun gear 6, and the P1 planetary carrier 8 and P1 ring gear 11 are in a free state, with no power transmission.

[0043] The specific power transmission is as follows: Motor 2 directly transmits power to P1 sun gear 6. P1 ring gear 11 is in a free state and has no constraint. P1 sun gear 6 drives P1 ring gear 11 to rotate freely. Power cannot be transmitted to output shaft 3 through P1 planetary carrier 8 and P2 planetary carrier 12. Power is interrupted at P1 ring gear 11, and the vehicle is in neutral with a transmission ratio of 0.

[0044] The drive system 101 includes a coaxially arranged motor 201 and a reduction mechanism. The motor 201 is a flat axial flux motor, replacing the cylindrical motor.

[0045] The reduction mechanism includes a compound gear mechanism and a shifting mechanism. The compound gear mechanism includes a planetary transmission assembly and a cylindrical gear assembly; the planetary transmission assembly and the shifting mechanism work together to achieve multiple gear switching.

[0046] The planetary transmission assembly includes a P1 sun gear 601, a P1 planet gear 701, a P1 planet carrier 801, a P2 sun gear 901, a P2 planet gear 110, a P1 ring gear 111, a P2 planet carrier 121, a P2 ring gear 131, and a housing 161.

[0047] The output shaft of motor 201 is connected to P1 sun gear 601. P1 planet gear 701 is mounted on P1 planet carrier 801. P1 planet carrier 801 is a rotating frame that supports P1 planet gear 701 and transmits power. P1 sun gear 601 meshes externally with P1 planet gear 701, and P1 planet gear 701 meshes internally with P1 gear ring 111.

[0048] Planetary carrier 801 (P1) is connected to sun gear 901 (P2). Planet gear 110 (P2) is mounted on planetary carrier 121 (P2). Sun gear 901 meshes externally with planet gear 110, while planet gear 110 meshes internally with ring gear 131 (P2). Planetary carrier 121 (P2) is a rotating frame that supports planet gear 110 and transmits power. Ring gear 131 (P2) is connected to housing 161, and planetary carrier 121 (P2) is connected to a cylindrical gear assembly for transmission.

[0049] The shifting mechanism includes a C1 shifting device 141 and a C2 shifting device 151. The C1 shifting device 141 is mounted on the P1 sun gear 601, and the C2 shifting device 151 is mounted on the P1 gear ring 111. The shifting mechanism can be a clutch or a synchronizer.

[0050] The C1 shifting device 141 is provided with a first synchronous ring, and the C2 shifting device 151 is provided with a second synchronous ring. Both the first and second synchronous rings are existing technologies and are not shown in the figure. When the system shifts gears, the first and second synchronous rings can achieve speed synchronization through friction.

[0051] The cylindrical gear assembly includes a driving gear 401 and a driven gear 501. The driving gear 401 is coaxially connected to the P2 planetary carrier 121. The driving gear 401 meshes with the driven gear 501. The driven gear 501 is connected to an output shaft 301, which is coaxially connected to the wheel.

[0052] The control methods for drive system 1 and drive system 101 are the same, and will not be described again here.

[0053] This invention employs two drive systems, mirror-oriented with their drive axes centered on the drive shafts, driving the wheels centrally to reduce eccentricity. A flat axial flux motor and reduction mechanism are coaxially arranged, saving axial dimensions. A composite transmission system combining planetary gears and cylindrical gears achieves a large transmission ratio with a simple structure and low cost. Three-speed ratio switching is achieved through the composite gear mechanism and shifting mechanism, facilitating convenient shifting to fully utilize motor performance. The cylindrical gear assembly enables an eccentric design for power input and output, combined with motor control to achieve electronic differential. Through the coordinated operation of the planetary gears and shifting mechanism, efficient and smooth multi-gear power distribution is achieved, suitable for the complex operating conditions of electric drive vehicles.

[0054] The above description provides examples of the preferred embodiments of the present invention. Parts not detailed herein are common knowledge to those skilled in the art. The scope of protection of the present invention is determined by the claims. Any equivalent modifications based on the technical teachings of the present invention are also within the scope of protection of the present invention.

Claims

1. A distributed multi-gear drive system with a central dual motor opposed configuration, characterized in that: The system comprises two driving systems (1, 101) for driving wheels, and the two driving systems (1, 101) are arranged in mirror image with the driving axis of the driving system as the center; The two driving systems (1, 101) respectively comprise a motor (2, 201) and a speed reduction mechanism arranged coaxially.

2. The distributed multi-gear driving system with a central double-motor opposite configuration according to claim 1, wherein: The motor (2, 201) is a flat axial flux motor.

3. The distributed multi-gear driving system with a central double-motor opposite configuration according to claim 1, wherein: The speed reduction mechanism comprises a compound gear mechanism and a gear shifting mechanism; The compound gear mechanism comprises a planetary transmission assembly and a cylindrical gear assembly, and the planetary transmission assembly and the gear shifting mechanism are combined to realize multiple gear shifting.

4. The distributed multi-gear driving system with a central double-motor opposite configuration according to claim 3, wherein: The planetary transmission assembly comprises a P1 sun gear (6, 601), a P1 planet gear (7, 701), a P1 planet carrier (8, 801), a P2 sun gear (9, 901), a P2 planet gear (10, 110), a P1 ring gear (11, 111), a P2 planet carrier (12, 121), a P2 ring gear (13, 131), and a housing (16, 161); The output shaft of the motor (2, 201) is connected to the P1 sun gear (6, 601), the P1 planet gear (7, 701) is arranged on the P1 planet carrier (8, 801), the P1 sun gear (6, 601) is externally meshed with the P1 planet gear (7, 701), and the P1 planet gear (7, 701) is internally meshed with the P1 ring gear (11, 111); The P1 planet carrier (8, 801) is coaxially connected to the P2 sun gear (9, 901), the P2 planet gear (10, 110) is arranged on the P2 planet carrier (12, 121), the P2 sun gear (9, 901) is externally meshed with the P2 planet gear (10, 110), and the P2 planet gear (10, 110) is internally meshed with the P2 ring gear (13, 131); The P2 ring gear (13, 131) is connected to the housing (16, 161), and the P2 planet carrier (12, 121) is drivingly connected to the cylindrical gear assembly.

5. The distributed multi-gear driving system with a central double-motor opposite configuration according to claim 4, wherein: The gear shifting mechanism comprises a C1 gear shifting device (14, 141) and a C2 gear shifting device (15, 151), the C1 gear shifting device (14, 141) is arranged on the P1 sun gear (6, 601), and the C2 gear shifting device (15, 151) is arranged on the P1 ring gear (11, 111); A first synchronous ring is arranged on the C1 gear shifting device (14, 141), and a second synchronous ring is arranged on the C2 gear shifting device (15, 151).

6. The distributed multi-gear driving system with a central double-motor opposite configuration according to claim 4, wherein: The cylindrical gear assembly comprises a driving wheel (4, 401) and a driven wheel (5, 501) in meshing; The driving wheel (4, 401) is coaxially connected with a P2 planetary carrier (12, 121), the driven wheel (5, 501) is coaxially connected with an output shaft (3, 301), and the output shaft (3, 301) is coaxially connected with a wheel.

7. The control method of the distributed multi-gear drive system with the central dual-motor opposed configuration according to claims 1-6, characterized in that, It comprises:

1. The gear shifting step controls the second synchronizer ring to move left and connect with the housing (16, 161), the C2 gear shifting device (15, 151) locks the housing (16, 161), the P1 planetary gear (7, 701) rotates around the P1 sun gear (6, 601), the P1 sun gear (6, 601) drives the P1 planetary gear (7, 701) to rotate, the P1 planetary gear (7, 701) drives the P1 planetary carrier (8, 801) to rotate, the P1 planetary carrier (8, 801) drives the P2 sun gear (9, 901) to rotate, the P2 sun gear (9, 901) drives the P2 planetary gear (10, 110) to rotate, the P2 planetary gear (10, 110) drives the P2 planetary carrier (12, 121) to rotate, and the power is output at a reduced speed through the P2 planetary carrier (12, 121).

8. The control method according to claim 7, characterized by, It also comprises:

2. The gear shifting step controls the second synchronizer ring to move right and connect with the P2 planetary carrier (12, 121), the P1 sun gear (6, 601) drives the P1 planetary gear (7, 701) to rotate, the P1 planetary gear (7, 701) drives the P1 ring gear (11, 111) and the P1 planetary carrier (8, 801) to rotate; the P1 planetary carrier (8, 801) rotates together with the P2 sun gear (9, 901), the P2 sun gear (9, 901) drives the P2 planetary gear (10, 110) to rotate, the P2 planetary gear (10, 110) drives the P2 planetary carrier (12, 121) to rotate, the P1 ring gear (11, 111) rotates together with the P2 planetary carrier (12, 121), and the power is transmitted through the P2 planetary carrier (12, 121).

9. The control method according to claim 7, characterized by, It also comprises:

3. The gear shifting step controls the first synchronizer ring to move right and connect with the P1 ring gear (11, 111), the P1 ring gear (11, 111) and the P1 sun gear (6, 601) are connected as one component, the P2 sun gear (9, 901) drives the P2 planetary gear (10, 110) to rotate, and the P2 planetary gear (10, 110) drives the P2 planetary carrier (12, 121) to rotate and transmit power.

10. The control method according to claim 7, characterized by, It also comprises: The neutral gear shifting step controls the first synchronizer ring to move left to a free state, the C1 gear shifting device (14, 141) locks the P1 sun gear (6, 601), the P1 planetary carrier (8, 801) and the P1 ring gear (11, 111) are in a free state, and no power is transmitted.

Images