Torque vector distribution system adopting parallel shaft structure

Abstract

The invention discloses a torque vector distribution system adopting a parallel shaft structure, which comprises a differential mechanism, a left half shaft is arranged on one side of the differential mechanism, a right half shaft is arranged on the other side of the differential mechanism, a vector motor is arranged on one side of the differential mechanism, a motor shaft of the vector motor is parallel to the left half shaft, a driven gear is sleeved on the left half shaft, and a driven gear is sleeved on the driven gear. The vector motor transmits power to the driven gear through a linkage assembly, and the driven gear transmits power to the left half shaft and a shell of the differential mechanism through a transmission assembly. The motor has a torque distribution function, the vector motor is arranged through a parallel shaft structure, the axial size can be greatly reduced, reasonable layout is facilitated, the dynamic property and economical efficiency of the whole vehicle are considered to the maximum extent, and the structure can be more compact.

Description

Technical Field

[0001] The present invention relates to the technical field of automobile power chassis, and in particular to a torque vector distribution system adopting a parallel axis structure. Background Art

[0002] Automobile safety performance is an important topic in automobile research. As one of the representative technologies of automobile active safety technology, the Electronic Stability Program (ESP) applies braking force to the wheels on one side of the car to generate additional yaw torque to control the vehicle dynamically and improve the handling stability of the car. Since ESP uses the principle of differential braking to control the vehicle, it will have a negative impact on the vehicle's driving performance and economy during operation, causing power loss. Therefore, researchers proposed torque vector distribution technology to solve the energy consumption and driving experience problems in vehicle yaw dynamics control.

[0003] For example, the authorization announcement number CN106195193B discloses a dual-clutch planetary electric differential, which relates to the field of automotive technology, including a main differential, a dual planetary gear planetary gear, a torque distribution left planetary gear, a torque distribution right planetary gear, a reduction planetary gear, a power clutch, a torque distribution clutch and a motor; by controlling the engagement and separation of the torque distribution clutch and the power clutch, the switching of different working modes can be achieved. However, the layout of the automobile differential is unreasonable. When it is in a high turn or on a road with poor adhesion conditions or in a bad state, its stability is poor, and it is prone to slipping, side sliding and poor climbing ability, which poses a great safety hazard. Traditional brakes cannot meet the high-precision torque response control requirements of the whole vehicle. In addition, in the industry, the motor is usually set on one side of the first semi-axle, and its motor shaft is set parallel to the first semi-axle. Such a layout leads to a large radial space occupation, limited vehicle layout, and is not conducive to a reasonable layout, which has great limitations. Summary of the invention

[0004] The purpose of the present invention is to overcome the deficiencies of the prior art and provide a torque vector distribution system using a parallel shaft structure.

[0005] The purpose of the present invention is achieved through the following technical solutions: A torque vector distribution system adopting a parallel shaft structure includes a differential, wherein a left half shaft is provided on one side of the differential, and a right half shaft is provided on the other side of the differential, a vector motor is provided on one side of the differential, a motor shaft of the vector motor is parallel to the left half shaft, a driven gear is sleeved on the left half shaft, the vector motor transmits power to the driven gear through a linkage assembly, and the driven gear transmits power to the left half shaft and a differential housing respectively through a transmission assembly; the transmission assembly includes a first planetary row and a second planetary row, the first planetary row and the second planetary row share a same planet carrier, a first ring gear of the first planetary row is fixedly connected to the left half shaft, and a second ring gear of the second planetary row is fixedly connected to the differential housing; the first planetary row includes a first sun gear, a first planetary gear meshing with the first sun gear is provided between the first ring gear and the first sun gear; the second planetary row includes a second sun gear, a second planetary gear meshing with the second sun gear is provided between the second ring gear and the second sun gear.

[0006] Preferably, the first sun gear and the driven gear are fixed to each other; the second sun gear is pivotally arranged on the torque transfer mechanism housing, and the second planetary gear is coaxially connected to the first planetary gear through the planet carrier.

[0007] Preferably, the planet carrier is located inside the second planetary gear and the first planetary gear, and is pivotally connected to both.

[0008] Preferably, the planet carrier is located outside the second planetary gear and the first planetary gear, and the first ring gear and the second ring gear are arranged back to back.

[0009] Preferably, the second sun gear and the driven gear are fixed to each other; the first sun gear is pivotally arranged on the torque transfer mechanism housing, and the second planetary gear and the first planetary gear are coaxially connected via a planet carrier.

[0010] Preferably, the planet carrier is located inside the second planetary gear and the first planetary gear, and is pivotally connected to both.

[0011] Preferably, the planet carrier is located outside the second planetary gear and the first planetary gear, and the first ring gear and the second ring gear are arranged back to back.

[0012] Preferably, the linkage assembly includes a linkage shaft arranged between the left half shaft and the motor shaft of the vector motor, and a linkage gear and a transmission gear are fixed on the linkage shaft. The linkage gear is meshed with a driving gear fixed on the motor shaft of the vector motor, and the transmission gear is meshed with the driven gear.

[0013] Preferably, the linkage assembly includes a driving gear fixedly mounted on the motor shaft of the vector motor, and an idler gear meshing with the driving gear and the driven gear is provided between the driving gear and the driven gear.

[0014] Preferably, hubs are provided on the end sides of the left half shaft and the right half shaft.

[0015] Preferably, the differential is dynamically connected to a main power drive mechanism.

[0016] The beneficial effects of the present invention are mainly reflected in: 1. The system of the present invention has a torque distribution function, which takes into account the energy consumption problem and driving experience in yaw dynamics control; under the condition of the same specification of vector motor, it can enhance the torque of the car and improve the adhesion, so as to meet the driving conditions on highly curved roads or roads with poor adhesion conditions or in harsh conditions, and can effectively improve the economy, handling stability and active safety of the car.

[0017] 2. The double planetary gear system of the transmission assembly of the present invention shares a planet carrier, and the rotation speed of the planet carrier is lower than the rotation speed of the differential, which can make the drag torque smaller and the performance stronger; at the same time, it can also reduce the number of parts, further reduce the weight and enhance the heat dissipation capacity, and achieve overall lightweight.

[0018] 3. In the transmission assembly of the present invention, a gear ring is used for power output (i.e., the first gear ring is fixedly connected to the left half shaft for torque output, and the second gear ring is fixedly connected to the housing of the differential for torque output). This structure can lead to a larger speed ratio, which can significantly reduce the overall speed of the transmission assembly, greatly reduce heat generation, reduce oil oxidation and deterioration, reduce lubrication performance and rubber seal aging, and improve safety to the greatest extent.

[0019] 4. The scheme of the present invention arranges the vector motor through a parallel shaft structure, which can greatly reduce the axial size, facilitate reasonable layout, take into account the power and economy of the vehicle to the greatest extent, and make the structure more compact. In addition, the system makes little change to the traditional differential, has low modification cost, and has wide applicability.

[0020] 5. The invention solution makes little change to the traditional differential, has low modification cost and has wide applicability.

[0021] 6. In the solution of the present invention, the vector motor, the first planetary gear, the second planetary gear and the differential are all rigidly connected, which can maximize the control accuracy of the system, with a control accuracy of less than 10ms and a fast feedback speed. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The technical solution of the present invention is further described below in conjunction with the accompanying drawings: Figure 1 : A schematic structural diagram of the first embodiment of the present invention; Figure 2 : A schematic structural diagram of a second embodiment of the present invention; Figure 3 : A schematic structural diagram of a third embodiment of the present invention; Figure 4 : A schematic structural diagram of a fourth embodiment of the present invention; Figure 5 : A schematic structural diagram of a fifth embodiment of the present invention; Figure 6 : A schematic structural diagram of a sixth embodiment of the present invention; Figure 7 : A schematic structural diagram of a seventh embodiment of the present invention; Figure 8 : A schematic structural diagram of the eighth embodiment of the present invention. DETAILED DESCRIPTION

[0023] The present invention will be described in detail below in conjunction with the specific embodiments shown in the accompanying drawings. However, these embodiments are not limited to the present invention, and any structural, methodological, or functional changes made by a person skilled in the art based on these embodiments are all within the scope of protection of the present invention.

[0024] The present invention will be described in detail below with reference to the accompanying drawings and in conjunction with embodiments.

[0025] like Figures 1 to 8 As shown, the present invention discloses a torque vector distribution system using a parallel shaft structure, including a differential 1. Like the prior art, the differential is powered and connected to a main power drive mechanism, which can be electric, hybrid, or other feasible solutions.

[0026] A left half shaft 2 is disposed on one side of the differential 1, and a right half shaft 3 is disposed on the other side. The differential 1 is used to enable the wheels disposed on the left half shaft 2 and the right half shaft 3 to achieve different rotation speeds.

[0027] A vector motor 4 is provided on one side of the differential 1, and the vector motor 4 is electrically connected to the battery, and the motor shaft of the vector motor 4 is parallel to the left half shaft 2. In the present invention, the motor shaft of the vector motor 4 is arranged in parallel with the differential half shaft, which can greatly reduce the axial size, facilitate reasonable layout, take into account the power and economy of the whole vehicle to the greatest extent, and make the structure more compact. In addition, the system has little modification to the traditional differential, low modification cost, and wide applicability.

[0028] In the present invention, a driven gear 9 is sleeved on the left half shaft 2, and the vector motor 4 transmits power to the driven gear 9 through the linkage assembly 8. After the driven gear 9 receives the power, it transmits the power to the left half shaft 1 and the housing of the differential 1 respectively through the transmission assembly.

[0029] Specifically, the transmission assembly includes a first planetary gear 5 and a second planetary gear 6, and the first planetary gear 5 and the second planetary gear 6 share the same planetary carrier 7. By sharing a planetary carrier, the double planetary gears can also reduce the number of parts, further reduce weight and enhance heat dissipation capacity, achieve overall lightweight, and at the same time, reduce costs.

[0030] Of course, more importantly, according to the speed ratio equation, it can be found that the rotation speed of the planetary carrier in the present invention is lower than the differential speed. When the rotation speed of the planetary carrier is low, the movement of the planetary gear driven by it is relatively smoother, the meshing between the planetary gear and the half-shaft gear is more stable, the impact and loss during the power transmission process are reduced, so that the system does not need to overcome a large additional resistance to transmit power, and the drag torque will also be smaller. Furthermore, the reduction of drag torque means that the power output by the engine can be more effectively transmitted to the wheels. When the vehicle is turning, the differential can more flexibly adjust the rotation speed of the wheels on both sides, so that the speed difference between the inner wheel and the outer wheel is more in line with the actual driving needs, the steering of the vehicle is more precise and stable, and the phenomena of jamming and tail swinging during steering are reduced, thereby improving the vehicle's handling performance and driving safety.

[0031] In the first embodiment of the present invention, the first ring gear 51 of the first planetary gear set 5 is fixedly connected to the left half shaft 2, and the second ring gear 61 of the second planetary gear set 6 is fixedly connected to the housing of the differential 1. The above arrangement has a torque distribution function, taking into account the energy consumption problem and driving experience in yaw dynamics control; it can effectively improve the economy, handling stability and active safety of the car. The first ring gear is connected to the differential, which can reduce the intermediate transmission components and improve the structural rigidity. The second ring gear is directly connected to the left half shaft, shortening the power transmission path and reducing energy loss. In the present invention, the first ring gear and the second ring gear are respectively connected to the housing and the left half shaft of the differential 1 for power output. When the helical gear is used, the thrust bearing can be miniaturized and can be arranged on both sides of the connecting plate. No additional parts are required to guide the axial force of the ring gear. The first ring gear and the second ring gear can be radially fixed on the existing structure to improve the NVH performance. In addition, the ring gear is the largest diameter component in the planetary gear, while the planetary gear is smaller in size. According to the gear transmission principle, the power will be transmitted to the ring gear through the planetary gear, thereby obtaining a larger speed ratio. The ring gear is used for transmission in the transmission assembly, resulting in a larger speed ratio, which can reduce the overall speed of the entire transmission assembly, greatly reduce the generation of heat, reduce the oxidation and deterioration of the oil, reduce the lubrication performance and the aging of the rubber seal, and maximize the safety. This is an unparalleled advantage in the existing technology.

[0032] like Figure 1 The figure shows the first embodiment of the present invention. Specifically, the first planetary row 5 includes a first sun gear 52 fixedly connected to the driven gear 9, and the two can be fixedly connected by a fixed hollow shaft. A first planetary gear 53 meshing with the first sun gear 51 and the first sun gear 52 is provided between the first gear ring 51 and the first sun gear 52; the second planetary row 6 includes a second sun gear 62 pivotally arranged on the torque transfer mechanism housing, a second planetary gear 63 meshing with the second sun gear 62 is provided between the second gear ring 61 and the second sun gear 62, and the second planetary gear 63 is coaxially connected with the first planetary gear 53 through the planet carrier 7.

[0033] The linkage assembly 8 includes a linkage shaft 81 arranged between the left half shaft 2 and the motor shaft of the vector motor 4, and a linkage gear 82 and a transmission gear 83 are fixedly provided on the linkage shaft 81. The linkage gear 82 is meshed with the driving gear 41 fixedly arranged on the motor shaft of the vector motor 4, and the transmission gear 83 is meshed with the driven gear 9.

[0034] In the first embodiment, the planet carrier 7 is located inside the second planet gear 63 and the first planet gear 53 and is connected to both.

[0035] The working process of the first embodiment is briefly described below: When the vehicle is running normally, the first planetary gear 5 and the second planetary gear 6 are idling without load, and the vector motor 4 is not running.

[0036] When the vehicle is turning, there is a speed difference between the left and right half shafts, the vector motor 4 is started, and the driving gear 41 on the motor shaft drives the linkage gear 82 to rotate, the linkage gear 82 rotates and drives the transmission gear 83 to rotate through the linkage shaft 81, the transmission gear 83 rotates and drives the first sun gear 52 to rotate through the driven gear, the first sun gear 52 rotates and drives the first planetary gear 53 meshed with it to rotate, the first planetary gear 53 rotates and transmits power to the first ring gear 51 and transmits power to the second planetary gear 63 through the planet carrier 7, the first ring gear 51 drives the left half shaft 2 to rotate; the second planetary gear 63 transmits power to the housing of the differential 1 through the second ring gear 61 meshed with it, so that a "differential torque" effect is formed between the two half shafts of the differential. .

[0037] like Figure 2 FIG. 2 is a second embodiment of the present invention, which is different from the first embodiment in that the planet carrier is arranged in a position, the planet carrier 7 is located outside the second planetary gear 63 and the first planetary gear 53, and the first gear ring 51 and the second gear ring 61 are arranged opposite to each other. The working process is similar to that of the first embodiment, and will not be described in detail here.

[0038] like Figure 3 The third embodiment of the present invention is shown in FIG. 1 . Specifically, the first planetary row 5 includes a first sun gear 52 fixedly connected to the driven gear 9, and a first planetary gear 53 meshing with the first sun gear 51 and the first sun gear 52 is provided between the first gear ring 51 and the first sun gear 52; the second planetary row 6 includes a second sun gear 62 pivotally arranged on the torque transfer mechanism housing, and a second planetary gear 63 meshing with the second sun gear 62 is provided between the second gear ring 61 and the second sun gear 62, and the second planetary gear 63 is coaxially connected with the first planetary gear 53 through the planet carrier 7. The linkage assembly 8 includes a driving gear 41 fixedly arranged on the motor shaft of the vector motor 4, and an idler gear 89 meshing with the driven gear 9 is provided between the driving gear 41 and the driven gear 9.

[0039] In the third embodiment, the planet carrier 7 is located inside the second planet gear 63 and the first planet gear 53 and is connected to both.

[0040] The working process of the third embodiment is briefly described below: When the vehicle is running normally, the first planetary gear 5 and the second planetary gear 6 are idling without load, and the vector motor 4 is not running.

[0041] When the vehicle is turning, a speed difference occurs between the left and right half shafts, and the vector motor 4 is started, and the idler gear 89 is driven to rotate through the driving gear 41 on the motor shaft. The idler gear 89 rotates to drive the transmission gear 83 to rotate, and the driven gear rotates to drive the first sun gear 52 to rotate. The first sun gear 52 rotates to drive the first planetary gear 53 meshing therewith to rotate. The first planetary gear 53 rotates to transmit power to the first ring gear 51 and to the second planetary gear 63 through the planetary carrier 7. The first ring gear 51 drives the left half shaft 2 to rotate; the second planetary gear 63 transmits power to the housing of the differential 1 through the second ring gear 61 meshing therewith, so that a "differential torque" effect is formed between the two half shafts of the differential.

[0042] like Figure 4 The fourth embodiment of the present invention is shown in FIG. 1 , which is different from the third embodiment in that the planet carrier is arranged in a position, the planet carrier 7 is located outside the second planetary gear 63 and the first planetary gear 53, and the first gear ring 51 and the second gear ring 61 are arranged opposite to each other. The working process is similar to that of the third embodiment, and will not be described in detail here.

[0043] In the first to fourth embodiments, a disconnect device is provided between the driven gear 9 and the first sun gear 52, or in another form: a disconnect device is provided between the torque transfer mechanism housing and the second sun gear 62, and the disconnect device is used to transmit or interrupt the torque transmission in the system. The disconnect device can be a dog clutch, a sliding clutch, or a friction clutch. Of course, it can also be other structures. The specific working process will be described in detail later.

[0044] like Figure 5 The fifth embodiment of the present invention is shown in FIG. 1 . Specifically, the first planetary row 5 includes a first sun gear 52 pivotally arranged on the torque transfer mechanism housing, and a first planetary gear 53 meshing with the first sun gear 51 and the first sun gear 52 is provided between the first gear ring 51 and the first sun gear 52; the second planetary row 6 includes a second sun gear 62 fixedly connected to the driven gear 9, and a second planetary gear 63 meshing with the second sun gear 62 is provided between the second gear ring 61 and the second sun gear 62, and the second planetary gear 63 and the first planetary gear 53 are coaxially connected through a planet carrier 7. The linkage assembly 8 includes a linkage shaft 81 arranged between the left half shaft 2 and the motor shaft of the vector motor 4, and a linkage gear 82 and a transmission gear 83 are fixedly arranged on the linkage shaft 81, and the linkage gear 82 meshes with the driving gear 41 fixedly arranged on the motor shaft of the vector motor 4, and the transmission gear 83 meshes with the driven gear 9.

[0045] In the fifth embodiment, the planet carrier 7 is located inside the second planetary gear 63 and the first planetary gear 53 and is connected to both.

[0046] The working process of the fifth embodiment is briefly described below: When the vehicle is running normally, the first planetary gear 5 and the second planetary gear 6 are idling without load, and the vector motor 4 is not running.

[0047] When the vehicle is turning, a speed difference occurs between the left and right half shafts, and the vector motor 4 is started, and the driving gear 41 on the motor shaft drives the linkage gear 82 to rotate. The linkage gear 82 rotates and drives the transmission gear 83 to rotate through the linkage shaft 81. The transmission gear 83 rotates and drives the second sun gear 62 to rotate through the driven gear. The second sun gear 62 rotates and drives the second planetary gear 63 meshing therewith to rotate. The second planetary gear 63 rotates to transmit power to the second ring gear 61 and to the first planetary gear 53 through the planetary carrier 7. The second ring gear 61 drives the left half shaft 2 to rotate; the first planetary gear 53 transmits power to the housing of the differential 1 through the first ring gear 51 meshing therewith, so that a "differential torque" effect is formed between the two half shafts of the differential.

[0048] like Figure 6 FIG. 6 is a sixth embodiment of the present invention, which is different from the fifth embodiment in that the planet carrier is arranged in a position, the planet carrier 7 is located outside the second planetary gear 63 and the first planetary gear 53, and the first gear ring 51 and the second gear ring 61 are arranged opposite to each other. The working process is similar to that of the fifth embodiment, and will not be described in detail here.

[0049] like Figure 7 The seventh embodiment of the present invention is shown in FIG. 5 . Specifically, the first planetary row 5 includes a first sun gear 52 pivotally mounted on the torque transfer mechanism housing, and a first planetary wheel 53 meshing with the first sun gear 51 and the first sun gear 52 is provided between the first gear ring 51 and the first sun gear 52; the second planetary row 6 includes a second sun gear 62 fixedly connected to the driven gear 9, and a second planetary wheel 63 meshing with the second sun gear 62 is provided between the second gear ring 61 and the second sun gear 62, and the second planetary wheel 63 and the first planetary wheel 53 are coaxially connected through a planet carrier 7. The linkage assembly 8 includes a driving gear 41 fixedly mounted on the motor shaft of the vector motor 4, and an idler wheel 89 meshing with the driven gear 9 is provided between the driving gear 41 and the driven gear 9.

[0050] In the seventh embodiment, the planet carrier 7 is located inside the second planet gear 63 and the first planet gear 53 and is connected to both.

[0051] The working process of the seventh embodiment is briefly described below: When the vehicle is running normally, the first planetary gear 5 and the second planetary gear 6 are idling without load, and the vector motor 4 is not running.

[0052] When the vehicle is turning, a speed difference occurs between the left and right half shafts, and the vector motor 4 is started, and the idler gear 89 is driven to rotate through the driving gear 41 on its motor shaft. The idler gear 89 rotates to drive the transmission gear 83 to rotate, and the driven gear rotates to drive the second sun gear 62 to rotate. The second sun gear 62 rotates to drive the second planetary gear 63 meshing therewith to rotate. The second planetary gear 63 rotates to transmit power to the second ring gear 61 and to the first planetary gear 53 through the planet carrier 7. The second ring gear 61 drives the left half shaft 2 to rotate; the first planetary gear 53 transmits power to the housing of the differential 1 through the first ring gear 51 meshing therewith, so that a "differential torque" effect is formed between the two half shafts of the differential.

[0053] like Figure 8 The eighth embodiment of the present invention is shown in FIG. 8 , which is different from the seventh embodiment in that the planet carrier is arranged in a position, the planet carrier 7 is located outside the second planetary gear 63 and the first planetary gear 53, and the first gear ring 51 and the second gear ring 61 are arranged opposite to each other. The working process is similar to the seventh embodiment, and will not be described in detail here.

[0054] In the fifth to eighth embodiments, a disconnect device or a driven gear 9 is provided between the torque transfer mechanism housing and the first sun gear 52 , or in another form: a disconnect device is provided between the second sun gear 62 .

[0055] The embodiments of the present invention are all provided with the disconnecting device, and the use of the disconnecting device is the preferred embodiment of the present invention. The disconnecting device is a claw clutch, a sleeve clutch or a friction clutch, and of course, it can also be other structures, all of which belong to the protection scope of the present invention.

[0056] The disconnect device allows a portion of the system to be disengaged, which helps to eliminate mechanical losses associated with the rotation of various unused components, thereby improving the overall efficiency of the system.

[0057] The disconnect device is controlled by an actuator, which is, for example, electromechanical, electromagnetic or hydraulic.

[0058] At present, the industry usually equips the auxiliary drive system with the disconnect device. When the permanent magnet motor is used as the auxiliary motor of the auxiliary drive system on the vehicle, in the non-powered working state, in order to prevent the auxiliary drive system from generating reverse rotation torque (that is, the rotor of the permanent magnet motor will follow the rotation of the differential housing and cut the magnetic lines of force), the disconnect device in the auxiliary drive system will disconnect the permanent magnet motor from the differential housing. In order to save energy consumption of the whole vehicle, when the vehicle is running at high speed, the disconnect device can disconnect the permanent magnet motor on the auxiliary drive system from the differential housing, that is: the auxiliary drive system and the differential housing do not transmit power, and the left and right half shafts run normally at high speed.

[0059] When the torque vector distribution system with a parallel shaft structure is used in conjunction with the vehicle auxiliary drive system, when the vehicle is in a high-speed forward state, if the disconnect device on the auxiliary drive system is disconnected, the left half shaft or the right half shaft and the differential housing will have a speed difference of more than 1000RPM. Due to the rigid connection and speed ratio of the vector motor, the first planetary gear, the second planetary gear and the differential, the vector motor will continue to operate at a speed of more than 20000RPM. Long-term high-speed operation will have a significant adverse effect on the thermal balance performance, efficiency and reliability of the torque vector distribution system with a parallel shaft structure. Therefore, the disconnect device of the torque vector distribution system with a parallel shaft structure also needs to be disconnected.

[0060] Of course, in the embodiment of the present invention, the disconnecting device may not be provided. In this way, the vector motor, the first planetary gear, the second planetary gear and the differential are all rigidly connected, which can maximize the feedback speed of the system.

[0061] It should be understood that although this specification is described according to implementation modes, not every implementation mode contains only one independent technical solution. This description of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each implementation mode may also be appropriately combined to form other implementation modes that can be understood by those skilled in the art.

[0062] The series of detailed descriptions listed above are only specific descriptions of feasible implementation methods of the present invention. They are not intended to limit the scope of protection of the present invention. Any equivalent implementation methods or changes that do not deviate from the technical spirit of the present invention should be included in the scope of protection of the present invention.

Claims

1. A torque vector distribution system adopting a parallel shaft structure, comprising a differential (1), wherein one side of the differential (1) is provided with a left half shaft (2), and the other side of the differential (1) is provided with a right half shaft (3), characterized in that: A vector motor (4) is provided on one side of the differential (1); the motor shaft of the vector motor (4) is parallel to the left half shaft (2); a driven gear (9) is sleeved on the left half shaft (2); the vector motor (4) transmits power to the driven gear (9) through a linkage assembly (8); the driven gear (9) transmits power to the left half shaft (2) and the housing of the differential (1) respectively through a transmission assembly; the transmission assembly comprises a first planetary gear (5) and a second planetary gear (6); the first planetary gear (5) and the second planetary gear (6) share the same planet carrier ( 7), the first ring gear (51) of the first planetary row (5) is fixedly connected to the left half shaft (2), and the second ring gear (61) of the second planetary row (6) is fixedly connected to the housing of the differential (1); the first planetary row (5) includes a first sun gear (52), and a first planetary gear (53) meshing with the first sun gear (51) and the first sun gear (52) is provided between the first ring gear (51) and the first sun gear (52); the second planetary row (6) includes a second sun gear (62), and a second planetary gear (63) meshing with the second sun gear (62) is provided between the second ring gear (61) and the second sun gear (62).

2. The torque vector distribution system using a parallel axis structure according to claim 1, characterized in that: The first sun gear (52) and the driven gear (9) are fixedly arranged with each other; the second sun gear (62) is pivotally arranged on a torque transfer mechanism housing, and the second planetary gear (63) and the first planetary gear (53) are coaxially connected via the planet carrier (7).

3. The torque vector distribution system using a parallel axis structure according to claim 2, characterized in that: The planet carrier (7) is located inside the second planetary gear (63) and the first planetary gear (53), and is pivotally connected to the two.

4. The torque vector distribution system using a parallel axis structure according to claim 2, characterized in that: The planet carrier (7) is located outside the second planetary gear (63) and the first planetary gear (53), and the first ring gear (51) and the second ring gear (61) are arranged opposite to each other.

5. The torque vector distribution system using a parallel axis structure according to claim 1, characterized in that: The second sun gear (62) and the driven gear (9) are fixedly arranged with each other; the first sun gear (52) is pivotally arranged on a housing of the torque transfer mechanism, and the second planetary gear (63) and the first planetary gear (53) are coaxially connected via a planet carrier (7).

6. The torque vector distribution system using a parallel axis structure according to claim 5, characterized in that: The planet carrier (7) is located inside the second planetary gear (63) and the first planetary gear (53), and is pivotally connected to the two.

7. The torque vector distribution system using a parallel axis structure according to claim 5, characterized in that: The planet carrier (7) is located outside the second planetary gear (63) and the first planetary gear (53), and the first ring gear (51) and the second ring gear (61) are arranged opposite to each other.

8. The torque vector distribution system using a parallel axis structure according to claim 1, characterized in that: The linkage assembly (8) comprises a linkage shaft (81) arranged between the left half shaft (2) and the motor shaft of the vector motor (4); a linkage gear (82) and a transmission gear (83) are fixedly provided on the linkage shaft (81); the linkage gear (82) meshes with a driving gear (41) fixedly provided on the motor shaft of the vector motor (4); and the transmission gear (83) meshes with the driven gear (9).

9. The torque vector distribution system using a parallel axis structure according to claim 1, characterized in that: The linkage assembly (8) comprises a driving gear (41) fixedly mounted on the motor shaft of the vector motor (4), and an idler gear (89) meshing with the driving gear (41) and the driven gear (9) is provided between the driving gear (41) and the driven gear (9).

10. The torque vector distribution system using a parallel axis structure according to claim 1, characterized in that: Hubs are provided on the end sides of the left half shaft (2) and the right half shaft (3).

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