Dual-motor planetary hybrid transmission for four-wheel drive vehicles

Abstract

A dual-motor planetary hybrid power transmission device for a four-wheel drive motor vehicle, wherein the ring gear of the first planetary gear mechanism is fixedly arranged in the rotor of the first drive motor and connected to the hollow transmission shaft, the transmission main shaft passes through the hollow transmission shaft to form a coaxial shaft, and forms a sliding fit with the hollow transmission shaft, the crankshaft of the engine is connected to the planetary carrier through the input shaft, the planetary carrier is connected to the transmission main shaft through the clutch, the sun gear shaft is loosely sleeved on the input shaft to form a coaxial shaft, the sun gear shaft is connected to the first brake, the active friction component of the first brake is fixed in the housing of the planetary hybrid power transmission device, the driven friction component is connected to the sun gear shaft, the output shaft is connected to the rear axle of the four-wheel drive motor vehicle, the transmission countershaft and the front axle transmission shaft are both arranged in parallel with the output shaft, the front axle transmission shaft is connected to the front axle of the four-wheel drive motor vehicle, the transmission countershaft passes through a hollow transmission countershaft to form a coaxial shaft, and forms a sliding fit with the hollow transmission countershaft.

Description

Technical Field

[0001] The invention relates to the field of hybrid electric vehicles, and in particular to a dual-motor planetary hybrid electric transmission device for a four-wheel drive motor vehicle. Background Art

[0002] At present, most hybrid vehicles use oil-electric hybrid transmission devices, and most oil-electric hybrid transmission devices use a dual-motor structure, that is, the oil-electric hybrid transmission device includes an engine powered by fuel and a drive motor powered by electricity, and also adds a generator. The generator uses the power of the motor vehicle to generate electricity and provide electricity for the motor vehicle. After the engine stops, the drive motor is used to drive the motor vehicle to reduce motor vehicle exhaust emissions and protect the environment. However, the connection and control between the engine, generator and drive motor have a direct impact on the driving performance of hybrid vehicles.

[0003] Since one motor in a common dual-motor hybrid system is only used to provide driving force and one motor is only used to generate electricity, the power of the motor used to provide driving force must meet all driving conditions of the car. The car has a large demand for motor power, so the drive motor is bulky and costly, which is extremely unfavorable for space layout.

[0004] The patent "A Hybrid Power Drive Device" with publication number CN111098688A discloses a hybrid power drive device, which includes a rear-drive component and a front-drive component. The rear-drive component includes a first motor and a transmission shaft, and the output shaft of the first motor is configured to selectively connect with the engine input shaft and the transmission shaft, and the transmission shaft is used to drive the rear axle; the front-drive component includes a second motor, and the second motor can drive the front axle. This hybrid power drive device has few drive gears, a simple four-wheel drive structure, and a fixed torque ratio distribution for front and rear drives. It cannot be used in all complex road conditions and can only be used on low-speed muddy roads. The use conditions are not comprehensive, which is not conducive to more abundant dynamic and economical power distribution. Summary of the invention

[0005] The purpose of the present invention is to address the corresponding deficiencies of the prior art and to provide a dual-motor planetary hybrid power transmission device for a four-wheel drive motor vehicle. A multi-speed transmission mechanism composed of a planetary gear mechanism and a gear transmission mechanism is used to distribute the power of the engine and the drive motor, greatly increasing the number of pure electric / fuel drive gears. Gear transmission and planetary mechanisms are used for power diversion, and torque is distributed to the front wheels through the output shaft. The drive motor is used to realize part-time four-wheel drive and full-time four-wheel drive functions. The device can be applied to vehicles with higher functional and environmental requirements, more effectively optimize fuel economy, and facilitate richer economical power distribution.

[0006] The objective of the present invention is achieved by adopting the following scheme: a dual-motor planetary hybrid power transmission device for a four-wheel drive motor vehicle comprises an engine, a first drive motor, and a second drive motor, a ring gear of a first planetary gear mechanism is fixedly arranged in a rotor of the first drive motor and connected to a hollow transmission shaft, a transmission main shaft passes through the hollow transmission shaft to form a coaxial shaft, and forms a sliding fit with the hollow transmission shaft, the crankshaft of the engine is connected to the planet carrier of the first planetary gear mechanism through an input shaft, the planet carrier of the first planetary gear mechanism is connected to the transmission main shaft through a clutch, the active friction component of the clutch is connected to the planet carrier of the first planetary gear mechanism, the driven friction component is connected to the transmission main shaft, and the planetary gear of the first planetary gear mechanism is arranged on the first planetary gear mechanism. A ring gear of a planetary gear mechanism and a sun gear of a first planetary gear mechanism, a sun gear shaft of the first planetary gear mechanism is sleeved on an input shaft to form a concentric shaft, the sun gear shaft of the first planetary gear mechanism is connected to a first brake, an active friction component of the first brake is fixed in a planetary hybrid power transmission device housing, a driven friction component is connected to the sun gear shaft of the first planetary gear mechanism, an output shaft and an input shaft and a transmission main shaft are all located on the same axis, the output shaft is connected to a rear axle of a four-wheel drive vehicle, a transmission countershaft and a front axle transmission shaft are both arranged in parallel with the output shaft, the front axle transmission shaft is connected to the front axle of the four-wheel drive vehicle, the transmission countershaft passes through a hollow transmission countershaft to form a concentric shaft, and forms a sliding fit with the hollow transmission countershaft;

[0007] The rotor of the second drive motor is loosely sleeved on the hollow transmission shaft, and the motor shaft of the second drive motor is connected to a hollow shaft, and the first gear is fixed to the hollow shaft in the circumferential direction;

[0008] A second gear is fixed circumferentially on the hollow transmission shaft, a third gear is provided on the transmission main shaft in an empty sleeve, and a first synchronizer is provided between the second gear and the third gear and is fixed circumferentially on the transmission main shaft;

[0009] The output shaft is provided with a fourth gear in an idler sleeve, a third synchronizer is provided between the third gear and the fourth gear and is circumferentially fixed on the output shaft, the left gear ring of the third synchronizer is circumferentially fixed on the transmission main shaft, and the output shaft is circumferentially fixed with a fifth gear and an eleventh gear;

[0010] The sixth gear is fixed circumferentially on the transmission countershaft, the tenth gear is arranged on the idle sleeve of the transmission countershaft, the seventh gear and the eighth gear are fixed circumferentially on the hollow transmission countershaft, the ninth gear and the twelfth gear are arranged on the idle sleeve of the hollow transmission countershaft, a fourth synchronizer is arranged between the ninth gear and the twelfth gear, a second synchronizer is arranged between the tenth gear and the twelfth gear, the second synchronizer is circumferentially fixed on the transmission countershaft, and the left gear ring of the second synchronizer is circumferentially fixed on the hollow transmission countershaft;

[0011] The front axle transmission shaft is connected to the transmission countershaft via a front axle first gear gear pair, and the front axle transmission shaft is connected to the hollow transmission countershaft via a front axle second gear gear pair;

[0012] The front axle first gear gear pair is composed of the sixth gear meshing with the thirteenth gear, and the front axle second gear gear pair is composed of the seventh gear meshing with the fourteenth gear;

[0013] The sixth gear is meshed with the first gear, the seventh gear is meshed with the second gear, the third gear is meshed with the eighth gear, the fourth gear is meshed with the ninth gear, the fifth gear is meshed with the tenth gear, and the eleventh gear is meshed with the twelfth gear.

[0014] Preferably, the thirteenth gear and the fourteenth gear are both arranged in an empty sleeve on the front axle drive shaft, a fifth synchronizer is arranged between the thirteenth gear and the fourteenth gear, and the fifth synchronizer is circumferentially fixed to the front axle drive shaft.

[0015] Preferably, the thirteenth gear and the fourteenth gear are connected to the front axle drive shaft through the second planetary gear mechanism, the sun gear shaft of the second planetary gear mechanism forms a sliding fit with the front axle drive shaft through a bearing, the thirteenth gear forms a sliding fit with the sun gear shaft of the second planetary gear mechanism through a bearing, the front axle drive shaft and the sun gear shaft of the second planetary gear mechanism are located on the same axis, the thirteenth gear is fixedly connected to the ring gear of the second planetary gear mechanism, the planetary gears of the second planetary gear mechanism are arranged between the ring gear of the second planetary gear mechanism and the sun gear of the second planetary gear mechanism, the planetary gears of the second planetary gear mechanism are connected to the front axle drive shaft through the planetary carrier of the second planetary gear mechanism, the planetary carrier of the second planetary gear mechanism is circumferentially fixed on the front axle drive shaft, and the fourteenth gear is circumferentially fixed on the sun gear shaft of the second planetary gear mechanism.

[0016] Preferably, the planet carrier of the second planetary gear mechanism is sleeved on the front axle drive shaft, and the sixth synchronizer is circumferentially fixed on the front axle drive shaft for controlling the power interruption between the second planetary gear mechanism and the front axle drive shaft.

[0017] Preferably, the planet carrier of the second planetary gear mechanism is connected to the front axle drive shaft via a second brake.

[0018] By adopting the above technical solution, the advantages of the present invention are as follows:

[0019] 1. In the technical solution of the present invention, the characteristics of the dual-motor drive and multi-speed transmission system are utilized. Compared with the prior art, the drive motor only needs to provide a smaller power to meet the driving requirements of the entire vehicle, which greatly reduces the size of the drive motor and saves the motor installation space of the hybrid vehicle.

[0020] 2. In the technical solution of the present invention, both motors have power driving and power generation functions. The two motors can cooperate with the engine simultaneously or separately to participate in the driving of the hybrid vehicle. During the gear change process, they can cooperate with each other to perform power compensation, and have richer hybrid function selection modes.

[0021] 3. The technical solution of the present invention can not only match vehicles with part-time four-wheel drive and full-time four-wheel drive functions according to the needs of the whole vehicle, but also can realize various different driving modes such as rear-wheel drive, part-time four-wheel drive, full-time four-wheel drive, etc. through the mutual cooperation of the fuel engine and two drive motors according to changes in external characteristics such as working conditions, road conditions, and environment.

[0022] 4. The present invention has a simple structure, clear functions of the participating functional components, low drive motor power, low cost, and is conducive to the integration and matching of hybrid power system vehicles;

[0023] 5. The technical solution of the present invention has good scalability, can achieve more reasonable modular and platform development, and can adapt to the requirements of more vehicle models. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present invention;

[0025] Figure 2 This is a schematic diagram of the structure of Embodiment 2 of the present invention;

[0026] Figure 3 This is a schematic diagram of the structure of Embodiment 3 of the present invention;

[0027] Figure 4 This is a schematic diagram of the structure of Example 4 of the present invention. DETAILED DESCRIPTION

[0028] like Figures 1 to 4As shown, a dual-motor planetary hybrid power transmission device for a four-wheel drive vehicle includes an engine 1, a first drive motor 2, and a second drive motor 3. The ring gear X3 of the first planetary gear mechanism is fixedly arranged in the rotor of the first drive motor 2 and connected to a hollow transmission shaft Z6. A transmission main shaft Z2 passes through the hollow transmission shaft Z6 to form a coaxial shaft and forms a sliding fit with the hollow transmission shaft Z6. The crankshaft of the engine 1 is connected to the planet carrier X4 of the first planetary gear mechanism through an input shaft Z1. The planet carrier X4 of the first planetary gear mechanism is connected to the transmission main shaft Z2 through a clutch C1. The active friction component of the clutch C1 is connected to the planet carrier X4 of the first planetary gear mechanism, and the driven friction component is connected to the transmission main shaft Z2. The planetary gear X2 of the first planetary gear mechanism is arranged on the ring gear X4 of the first planetary gear mechanism. 3 and the sun gear X1 of the first planetary gear mechanism, the sun gear shaft X6 of the first planetary gear mechanism is sleeved on the input shaft Z1 to form a coaxial shaft, the sun gear shaft X6 of the first planetary gear mechanism is connected to the first brake B1, the active friction component of the first brake B1 is fixed in the housing of the planetary hybrid power transmission device, the driven friction component is connected to the sun gear shaft X6 of the first planetary gear mechanism, an output shaft Z5 and the input shaft Z1 and the transmission main shaft Z2 are all located on the same axis, the output shaft Z5 is connected to the rear axle 4 of the four-wheel drive motor vehicle, a transmission countershaft Z3 and a front axle transmission shaft Z8 are all arranged in parallel with the output shaft Z5, the front axle transmission shaft Z8 is connected to the front axle 5 of the four-wheel drive motor vehicle, the transmission countershaft Z3 passes through a hollow transmission countershaft Z4 to form a coaxial shaft, and forms a sliding fit with the hollow transmission countershaft Z4;

[0029] The rotor of the second drive motor 3 is loosely sleeved on the hollow transmission shaft Z6, and the motor shaft of the second drive motor 3 is connected to a hollow shaft Z7, and the hollow shaft Z7 fixes the first gear G1 circumferentially;

[0030] A second gear G2 is fixed circumferentially on the hollow transmission shaft Z6, a third gear G3 is set in an empty sleeve on the transmission main shaft Z2, and a first synchronizer T1 is set between the second gear G2 and the third gear G3 and is fixed circumferentially on the transmission main shaft Z2;

[0031] The fourth gear G4 is set on the output shaft Z5, and the third synchronizer T3 is set between the third gear G3 and the fourth gear G4 and is circumferentially fixed on the output shaft Z5. The left gear ring of the third synchronizer T3 is circumferentially fixed on the transmission main shaft Z2, and the fifth gear G5 and the eleventh gear G11 are circumferentially fixed on the output shaft Z5.

[0032] The sixth gear G6 is fixed circumferentially on the transmission countershaft Z3, the tenth gear G10 is set in an empty sleeve on the transmission countershaft Z3, the seventh gear G7 and the eighth gear G8 are fixed circumferentially on the hollow transmission countershaft Z4, the ninth gear G9 and the twelfth gear G12 are set in an empty sleeve on the hollow transmission countershaft Z4, a fourth synchronizer T4 is set between the ninth gear G9 and the twelfth gear G12, a second synchronizer T2 is set between the tenth gear G10 and the twelfth gear G12, the second synchronizer T2 is circumferentially fixed on the transmission countershaft Z3, and the left ring gear of the second synchronizer T2 is circumferentially fixed on the hollow transmission countershaft Z4;

[0033] The front axle transmission shaft Z8 is connected to the transmission countershaft Z3 via a front axle first gear gear pair, and the front axle transmission shaft Z8 is connected to the hollow transmission countershaft Z4 via a front axle second gear gear pair;

[0034] The front axle first gear gear pair is composed of the sixth gear G6 meshing with the thirteenth gear G13, and the front axle second gear gear pair is composed of the seventh gear G7 meshing with the fourteenth gear G14;

[0035] The sixth gear G6 meshes with the first gear G1, the seventh gear G7 meshes with the second gear G3, the third gear G3 meshes with the eighth gear G8, the fourth gear G4 meshes with the ninth gear G9, the fifth gear G5 meshes with the tenth gear G10, and the eleventh gear G11 meshes with the twelfth gear G12.

[0036] In Embodiment 1, the thirteenth gear G13 and the fourteenth gear G14 are both loosely mounted on the front axle transmission shaft Z8, a fifth synchronizer T5 is disposed between the thirteenth gear G13 and the fourteenth gear G14, and the fifth synchronizer T5 is circumferentially fixed to the front axle transmission shaft Z8.

[0037] In Example 2, the thirteenth gear G13 and the fourteenth gear G14 are connected to the front axle drive shaft Z8 through the second planetary gear mechanism, the sun gear shaft Xz of the second planetary gear mechanism forms a sliding fit with the front axle drive shaft Z8 through a bearing, the thirteenth gear G13 forms a sliding fit with the sun gear shaft Xz of the second planetary gear mechanism through a bearing, the front axle drive shaft Z8 and the sun gear shaft Xz of the second planetary gear mechanism are located on the same axis, the thirteenth gear G13 is fixedly connected to the ring gear Xc of the second planetary gear mechanism, the planetary gear Xb of the second planetary gear mechanism is provided between the ring gear Xc of the second planetary gear mechanism and the sun gear Xa of the second planetary gear mechanism, the planetary gear Xb of the second planetary gear mechanism is connected to the front axle drive shaft Z8 through the planetary carrier Xd of the second planetary gear mechanism, the planetary carrier Xd of the second planetary gear mechanism is circumferentially fixed on the front axle drive shaft Z8, and the fourteenth gear G14 is circumferentially fixed on the sun gear shaft Xz of the second planetary gear mechanism.

[0038] Embodiment 3 is based on Embodiment 2, in which the planet carrier Xd of the second planetary gear mechanism is loosely mounted on the front axle drive shaft Z8, and the sixth synchronizer T6 is circumferentially fixed on the front axle drive shaft Z8 to control the power interruption between the second planetary gear mechanism and the front axle drive shaft Z8.

[0039] Embodiment 4 is based on Embodiment 2, in which the planet carrier Xd of the second planetary gear mechanism is connected to the front axle drive shaft Z8 via the second brake B2, and the second brake B2 is used to control the power interruption between the second planetary gear mechanism and the front axle drive shaft Z8.

[0040] For example, using the technical solution of embodiment 1, the operation mode of the hybrid vehicle is as follows:

[0041] Engine-only mode:

[0042] The power of the engine 1 can achieve multiple driving gears and realize the AMT automatic transmission function through the cooperation of the clutch C1, the brake B1, the first synchronizer T1, the second synchronizer T2, the third synchronizer T3, the fourth synchronizer T4, the fifth synchronizer T5, etc.

[0043] Four-wheel drive mode: rear drive power is output with a fixed torque ratio. When the second synchronizer T2 and the fifth synchronizer T5 are in gear, the front drive power can achieve a fixed torque ratio power output; when the second synchronizer T2 and the fifth synchronizer T5 are not in gear, the front drive cannot output power.

[0044] Pure electric mode:

[0045] The power of the first drive motor 2 cooperates with each other through the first synchronizer T1, the second synchronizer T2, the third synchronizer T3, and the fourth synchronizer T4, and can realize multiple pure electric drive gears. The gear selection can be performed according to the motor state and other requirements during the driving process. The power of the second drive motor 3 cooperates with each other through the first synchronizer T1, the second synchronizer T2, the third synchronizer T3, and the fourth synchronizer T4, and can realize multiple pure electric drive gears. The gear selection can be performed according to the motor state and other requirements during the driving process.

[0046] Four-wheel drive mode: the rear drive force is output with a fixed torque ratio; the front drive force can achieve power output with different torque ratios according to the needs of the front wheels by adjusting the drive motor when the fifth synchronizer T5 is in gear; when the fifth synchronizer T5 is not in gear, the front drive cannot output power.

[0047] Hybrid drive mode:

[0048] The power of the engine 1, the first drive motor 2, and the second drive motor 3 cooperate with each other through the clutch C1, the brake B1, the first synchronizer T1, the second synchronizer T2, the third synchronizer T3, and the fourth synchronizer T4 to achieve multiple fuel drive gears and multiple pure electric drive gears. During the driving process, the power of the first drive motor 2 and the second drive motor 3 can assist the power of the engine 1 to achieve gear shifting without power interruption. While the power is more sufficient, it has better comfort and smoothness.

[0049] Four-wheel drive mode: the rear drive force is output with a fixed torque ratio; when the fifth synchronizer T5 is in gear, the front drive force can be adjusted according to the needs of the front wheels through the drive motor and cooperate with the engine to achieve power output with different torque ratios; when the fifth synchronizer T5 is not in gear, the front drive cannot output power.

[0050] Idle mode:

[0051] Through the cooperation of the clutch C1, the brake B1, the first synchronizer T1 and the second synchronizer T2, multiple idle power generation gears can be selected, and the power of the engine can be used to generate electricity for the first drive motor 2 and the second drive motor 3 respectively through these different gear ratios.

[0052] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modification made to the present invention by those skilled in the art without departing from the spirit of the present invention shall fall within the protection scope of the present invention.

Claims

1. A dual-motor planetary hybrid power transmission device for a four-wheel drive vehicle, characterized in that: The invention comprises an engine (1), a first drive motor (2), and a second drive motor (3); a ring gear (X3) of a first planetary gear mechanism is fixedly arranged in a rotor of the first drive motor (2) and connected to a hollow transmission shaft (Z6); a transmission main shaft (Z2) passes through the hollow transmission shaft (Z6) to form a coaxial shaft and forms a sliding fit with the hollow transmission shaft (Z6); a crankshaft of the engine (1) is connected to a planet carrier (X4) of the first planetary gear mechanism via an input shaft (Z1); the planet carrier (X4) of the first planetary gear mechanism is connected to the transmission main shaft (Z2) via a clutch (C1); an active friction component of the clutch (C1) is connected to the planet carrier (X4) of the first planetary gear mechanism; a driven friction component is connected to the transmission main shaft (Z2); and a planetary gear (X2) of the first planetary gear mechanism is arranged between the ring gear (X3) of the first planetary gear mechanism and the sun gear of the first planetary gear mechanism. (X1), the sun gear shaft (X6) of the first planetary gear mechanism is loosely sleeved on the input shaft (Z1) to form a coaxial shaft, the sun gear shaft (X6) of the first planetary gear mechanism is connected to the first brake (B1), the active friction component of the first brake (B1) is fixed in the housing of the planetary hybrid power transmission device, the driven friction component is connected to the sun gear shaft (X6) of the first planetary gear mechanism, an output shaft (Z5) and the input shaft (Z1) and the transmission main shaft (Z2) are all located on the same axis, the output shaft (Z5) is connected to the rear axle (4) of the four-wheel drive motor vehicle, a transmission countershaft (Z3) and a front axle transmission shaft (Z8) are both arranged in parallel with the output shaft (Z5), the front axle transmission shaft (Z8) is connected to the front axle (5) of the four-wheel drive motor vehicle, the transmission countershaft (Z3) passes through a hollow transmission countershaft (Z4) to form a coaxial shaft, and forms a sliding fit with the hollow transmission countershaft (Z4); The rotor of the second drive motor (3) is loosely sleeved on a hollow transmission shaft (Z6); the motor shaft of the second drive motor (3) is connected to a hollow shaft (Z7), and the first gear (G1) is fixed to the hollow shaft (Z7) in the circumferential direction; A second gear (G2) is fixed circumferentially on the hollow transmission shaft (Z6), a third gear (G3) is provided in an empty sleeve on the transmission main shaft (Z2), and a first synchronizer (T1) is provided between the second gear (G2) and the third gear (G3) and is fixed circumferentially on the transmission main shaft (Z2); A fourth gear (G4) is provided in an empty sleeve on the output shaft (Z5); a third synchronizer (T3) is provided between the third gear (G3) and the fourth gear (G4) and is circumferentially fixed on the output shaft (Z5); a left gear ring of the third synchronizer (T3) is circumferentially fixed on the transmission main shaft (Z2); and a fifth gear (G5) and an eleventh gear (G11) are circumferentially fixed on the output shaft (Z5); A sixth gear (G6) is circumferentially fixed on the transmission countershaft (Z3), a tenth gear (G10) is provided in an empty sleeve on the transmission countershaft (Z3), a seventh gear (G7) and an eighth gear (G8) are circumferentially fixed on the hollow transmission countershaft (Z4), a ninth gear (G9) and a twelfth gear (G12) are provided in an empty sleeve on the hollow transmission countershaft (Z4), a fourth synchronizer (T4) is provided between the ninth gear (G9) and the twelfth gear (G12), a second synchronizer (T2) is provided between the tenth gear (G10) and the twelfth gear (G12), the second synchronizer (T2) is circumferentially fixed on the transmission countershaft (Z3), and a left gear ring of the second synchronizer (T2) is circumferentially fixed on the hollow transmission countershaft (Z4); The front axle drive shaft (Z8) and the transmission countershaft (Z3) are connected via a front axle first gear pair, and the front axle drive shaft (Z8) and the hollow transmission countershaft (Z4) are connected via a front axle second gear pair; The front axle first gear gear pair is composed of a sixth gear (G6) meshing with a thirteenth gear (G13), and the front axle second gear gear pair is composed of a seventh gear (G7) meshing with a fourteenth gear (G14); The sixth gear (G6) meshes with the first gear (G1), the seventh gear (G7) meshes with the second gear (G2), the third gear (G3) meshes with the eighth gear (G8), the fourth gear (G4) meshes with the ninth gear (G9), the fifth gear (G5) meshes with the tenth gear (G10), and the eleventh gear (G11) meshes with the twelfth gear (G12).

2. The dual-motor planetary hybrid power transmission device according to claim 1, characterized in that: The thirteenth gear (G13) and the fourteenth gear (G14) are both arranged in an empty sleeve on the front axle drive shaft (Z8), a fifth synchronizer (T5) is arranged between the thirteenth gear (G13) and the fourteenth gear (G14), and the fifth synchronizer (T5) is circumferentially fixed to the front axle drive shaft (Z8).

3. The dual-motor planetary hybrid power transmission device according to claim 1, characterized in that: The thirteenth gear (G13) and the fourteenth gear (G14) are connected to the front axle drive shaft (Z8) through the second planetary gear mechanism, the sun gear shaft (Xz) of the second planetary gear mechanism forms a sliding fit with the front axle drive shaft (Z8) through a bearing, the thirteenth gear (G13) forms a sliding fit with the sun gear shaft (Xz) of the second planetary gear mechanism through a bearing, the front axle drive shaft (Z8) and the sun gear shaft (Xz) of the second planetary gear mechanism are located on the same axis, the thirteenth gear (G13) and the second planetary gear mechanism form a sliding fit with the sun gear shaft (Xz) of the second planetary gear mechanism The fourteenth gear (G14) is fixedly connected to the ring gear (Xc) of the second planetary gear mechanism, a planetary gear (Xb) of the second planetary gear mechanism is arranged between the ring gear (Xc) of the second planetary gear mechanism and the sun gear (Xa) of the second planetary gear mechanism, the planetary gear (Xb) of the second planetary gear mechanism is connected to the front axle drive shaft (Z8) through the planetary carrier (Xd) of the second planetary gear mechanism, the planetary carrier (Xd) of the second planetary gear mechanism is circumferentially fixed on the front axle drive shaft (Z8), and the fourteenth gear (G14) is circumferentially fixed on the sun gear shaft (Xz) of the second planetary gear mechanism.

4. The dual-motor planetary hybrid power transmission device according to claim 3, characterized in that: The planet carrier (Xd) of the second planetary gear mechanism is loosely mounted on the front axle drive shaft (Z8), and the sixth synchronizer (T6) is circumferentially fixed on the front axle drive shaft (Z8) for controlling the power interruption between the second planetary gear mechanism and the front axle drive shaft (Z8).

5. The dual-motor planetary hybrid power transmission device according to claim 3, characterized in that: The planet carrier (Xd) of the second planetary gear mechanism is connected to the front axle drive shaft (Z8) via a second brake (B2).

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