CN215360910U - Dual-motor planetary hybrid power transmission device for four-wheel drive motor vehicle - Google Patents
Dual-motor planetary hybrid power transmission device for four-wheel drive motor vehicle Download PDFInfo
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- CN215360910U CN215360910U CN202121472402.3U CN202121472402U CN215360910U CN 215360910 U CN215360910 U CN 215360910U CN 202121472402 U CN202121472402 U CN 202121472402U CN 215360910 U CN215360910 U CN 215360910U
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Abstract
A double-motor planetary hybrid power transmission device for a four-wheel drive motor vehicle is characterized in that a gear ring of a first planetary gear mechanism is fixedly arranged in a rotor of a first drive motor and connected with a hollow transmission shaft, a transmission main shaft penetrates through the hollow transmission shaft to form a concentric shaft and forms sliding fit with the hollow transmission shaft, a crankshaft of an engine is connected with a planet carrier through an input shaft, the planet carrier is connected with the transmission main shaft through a clutch, a sun gear shaft is sleeved on the input shaft in a hollow mode to form the concentric shaft, the sun gear shaft is connected with a first brake, a driving friction assembly of the first brake is fixed in a box body of the planetary hybrid power transmission device, a driven friction assembly is connected with the sun gear shaft, the output shaft is connected with a rear axle of the four-wheel drive motor vehicle, the transmission auxiliary shaft and a front axle are arranged in parallel with the output shaft, the front axle transmission shaft is connected with a front axle of the four-wheel drive motor vehicle, the transmission auxiliary shaft penetrates through a hollow transmission auxiliary shaft to form the concentric shaft, and the hollow transmission auxiliary shaft is in sliding fit with the hollow transmission auxiliary shaft.
Description
Technical Field
The utility model relates to the field of hybrid electric vehicles, in particular to a double-motor planetary hybrid power transmission device for a four-wheel drive electric vehicle.
Background
At present, most hybrid electric vehicles adopt oil-electricity hybrid power transmission devices, and most oil-electricity hybrid power transmission devices adopt a dual-motor structure, namely, the oil-electricity hybrid power transmission devices comprise an engine obtaining power from fuel oil and a driving motor running by electric power, and a generator is additionally arranged, the generator utilizes the power generated by the running of the motor vehicle to provide electric energy for the motor vehicle, and after the engine stops, the driving motor is utilized to drive the motor vehicle to run, so that the exhaust emission of the motor vehicle is reduced, and the environment is protected. The connection and control among the engine, the generator, and the driving motor have a direct influence on the traveling performance of the hybrid vehicle.
Because one motor in the common double-motor hybrid power device is only used for providing driving force, and one motor only generates electricity, the power of the motor used for providing the driving force must meet the running working conditions of all automobiles, and the automobile has large demand on the power of the motor, so that the driving motor is large in size and high in cost, and is extremely not beneficial to space arrangement.
Patent publication CN111098688A, a hybrid drive apparatus, discloses a hybrid drive apparatus, which includes a rear drive assembly and a front drive assembly, the rear drive assembly includes a first motor and a transmission shaft, an output shaft of the first motor is configured to be selectively in transmission connection with an input shaft of an engine and the transmission shaft, and the transmission shaft is used for driving a rear axle; the front drive assembly includes a second motor capable of driving the front axle. The hybrid power driving device has fewer driving gears and a simple four-wheel drive structure, the front and rear drives are distributed according to a fixed torque ratio, and the hybrid power driving device cannot be applied to all complex road working conditions, can be only used on low-speed muddy roads, cannot be used on incomplete working conditions and is not beneficial to richer power property and economical power distribution.
Disclosure of Invention
The utility model aims to overcome the corresponding defects in the prior art, and provides a double-motor planetary hybrid power transmission device for a four-wheel drive motor vehicle.
The purpose of the utility model is realized by adopting the following scheme: a double-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, wherein a gear ring of a first planetary gear mechanism is fixedly arranged in a rotor of the first drive motor and is connected with a hollow transmission shaft, a transmission main shaft penetrates through the hollow transmission shaft to form a concentric shaft and is in sliding fit with the hollow transmission shaft, a crankshaft of the engine is connected with a planet carrier of the first planetary gear mechanism through an input shaft, the planet carrier of the first planetary gear mechanism is connected with the transmission main shaft through a clutch, a driving friction assembly of the clutch is connected with the planet carrier of the first planetary gear mechanism, a driven friction assembly is connected with the transmission main shaft, a planet wheel of the first planetary gear mechanism is arranged between the gear ring of the first planetary gear mechanism and a sun wheel of the first planetary gear mechanism, the sun gear shaft of the first planetary gear mechanism is sleeved on the input shaft in a hollow mode to form a concentric shaft, the sun gear shaft of the first planetary gear mechanism is connected with a first brake, a driving friction assembly of the first brake is fixed in a planetary hybrid power transmission device box body, a driven friction assembly is connected with the sun gear shaft of the first planetary gear mechanism, an output shaft, the input shaft and a transmission main shaft are located on the same axial line, the output shaft is connected with a rear axle of the four-wheel drive motor vehicle, a transmission auxiliary shaft and a front axle transmission shaft are arranged in parallel with the output shaft, the front axle transmission shaft is connected with a front axle of the four-wheel drive motor vehicle, and the transmission auxiliary shaft penetrates through a hollow transmission auxiliary shaft to form a concentric shaft and forms sliding fit with the hollow transmission auxiliary shaft;
a rotor of the second driving motor is sleeved on the hollow transmission shaft in an empty mode, a motor shaft of the second driving motor is connected with a hollow shaft, and a first gear is fixed on the circumference of the hollow shaft;
a second gear is circumferentially fixed on the hollow transmission shaft, a third gear is arranged on the transmission main shaft in an empty sleeve mode, and a first synchronizer is arranged between the second gear and the third gear and is circumferentially fixed on the transmission main shaft;
a fourth gear is sleeved on the output shaft in an empty mode, a third synchronizer is arranged between the third gear and the fourth gear and fixed on the output shaft in the circumferential direction, a left gear ring of the third synchronizer is fixed on the transmission main shaft in the circumferential direction, and a fifth gear and an eleventh gear are fixed on the output shaft in the circumferential direction;
a sixth gear is circumferentially fixed on the transmission auxiliary shaft, a tenth gear is arranged on the transmission auxiliary shaft in an empty sleeve manner, a seventh gear and an eighth gear are circumferentially fixed on the hollow transmission auxiliary shaft, a ninth gear and a twelfth gear are arranged on the hollow transmission auxiliary shaft in an empty sleeve manner, 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 auxiliary shaft, and a left gear ring of the second synchronizer is circumferentially fixed on the hollow transmission auxiliary shaft;
the front axle transmission shaft is connected with the transmission auxiliary shaft through a front axle first gear pair, and the front axle transmission shaft is connected with the hollow transmission auxiliary shaft through a front axle second gear pair;
the front axle first gear pair is formed by meshing a sixth gear and a thirteenth gear, and the front axle second gear pair is formed by meshing a seventh gear and a fourteenth gear;
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.
Preferably, the thirteenth gear and the fourteenth gear are both sleeved on the front axle transmission shaft in an empty manner, a fifth synchronizer is arranged between the thirteenth gear and the fourteenth gear, and the fifth synchronizer is circumferentially fixed with the front axle transmission shaft.
Preferably, the thirteenth gear and the fourteenth gear are connected with the front axle transmission shaft through a second planetary gear mechanism, a sun gear shaft of the second planetary gear mechanism forms a sliding fit with the front axle transmission shaft through a bearing, the thirteenth gear forms a sliding fit with a sun gear shaft of the second planetary gear mechanism through a bearing, the front axle transmission shaft and the sun gear shaft of the second planetary gear mechanism are both located on the same axial line, the thirteenth gear is fixedly connected with a gear ring of the second planetary gear mechanism, a planet wheel of the second planetary gear mechanism is arranged between the gear ring of the second planetary gear mechanism and the sun gear of the second planetary gear mechanism, the planet wheel of the second planetary gear mechanism is connected with the front axle transmission shaft through a planet carrier of the second planetary gear mechanism, and the planet carrier of the second planetary gear mechanism is circumferentially fixed on the front axle transmission shaft, the fourteenth gear is circumferentially fixed to the sun gear shaft of the second planetary gear mechanism.
Preferably, the planet carrier of the second planetary gear mechanism is sleeved on the front axle transmission shaft, and the sixth synchronizer is circumferentially fixed on the front axle transmission shaft and used for controlling the power interruption of the second planetary gear mechanism and the front axle transmission shaft.
Preferably, the planet carrier of the second planetary gear mechanism is connected with the front axle transmission shaft through a second brake.
By adopting the technical scheme, the utility model has the advantages as follows:
1. in the technical scheme of the utility model, by utilizing the characteristics of the double-motor drive and multi-gear transmission system, compared with the prior art, the drive motor can meet the drive requirement of the whole automobile only by providing smaller power, thereby greatly reducing the volume of the drive motor and saving the motor installation space of the hybrid electric vehicle.
2. According to the technical scheme, the two motors have power driving and power generating functions, can be matched with the engine simultaneously or respectively to participate in driving the hybrid electric vehicle, can be matched with each other to perform power compensation in the gear changing process, and have richer hybrid function selection modes.
3. The technical scheme of the utility model not only can match the vehicles meeting the functions of time-sharing four-wheel drive and full-time four-wheel drive according to the requirements of the whole vehicle, but also can realize a plurality of different driving modes of rear drive, time-sharing four-wheel drive, full-time four-wheel drive and the like through the mutual matching of the fuel engine and the two driving motors according to the change of external characteristics such as working conditions, road conditions, environments and the like.
4. The utility model has simple structure, clear purpose of participating functional parts, small power of the driving motor and low cost, and is beneficial to the integrated matching of the hybrid power system vehicle;
5. the technical scheme of the utility model has good expansibility, can realize more reasonable modularization and platform development, and can meet the requirements of more vehicle types.
Drawings
FIG. 1 is a schematic structural view of example 1 of the present invention;
FIG. 2 is a schematic structural diagram of example 2 of the present invention;
FIG. 3 is a schematic structural diagram according to embodiment 3 of the present invention;
fig. 4 is a schematic structural diagram of embodiment 4 of the present invention.
Detailed Description
As shown in fig. 1 to 4, a dual motor planetary hybrid transmission for a four wheel drive motor vehicle includes an engine 1, a first drive motor 2, a second drive motor 3, a ring gear X3 of a first planetary gear mechanism fixedly disposed in a rotor of the first drive motor 2 and connected to a hollow transmission shaft Z6, a transmission main shaft Z2 formed a concentric shaft through the hollow transmission shaft Z6 and formed a sliding fit with the hollow transmission shaft Z6, a crankshaft of the engine 1 connected to a carrier X4 of the first planetary gear mechanism through an input shaft Z1, the carrier X4 of the first planetary gear mechanism connected to a transmission main shaft Z2 through a clutch C1, a driving friction assembly of the clutch C1 connected to a carrier X4 of the first planetary gear mechanism, a driven friction assembly connected to the transmission main shaft Z2, an X2 of the first planetary gear mechanism disposed between the ring gear X3 of the first planetary gear mechanism and a sun gear X1 of the first planetary gear mechanism, a sun gear shaft X6 of the first planetary gear mechanism is sleeved on an input shaft Z1 in an empty mode to form a concentric shaft, a sun gear shaft X6 of the first planetary gear mechanism is connected with a first brake B1, a driving friction component of the first brake B1 is fixed in a planetary hybrid power transmission device box, a driven friction component is connected with a sun gear shaft X6 of the first planetary gear mechanism, an output shaft Z5 is positioned on the same axial line with the input shaft Z1 and a transmission main shaft Z2, the output shaft Z5 is connected with a rear axle 4 of the four-wheel drive motor vehicle, a transmission auxiliary shaft Z3 and a front axle transmission shaft Z8 are arranged in parallel with the output shaft Z5, the front axle transmission shaft Z8 is connected with a front axle 5 of the four-wheel drive motor vehicle, and the transmission auxiliary shaft Z3 penetrates through a hollow transmission auxiliary shaft Z4 to form a concentric shaft and forms a sliding fit with the hollow auxiliary shaft transmission Z4;
the rotor of the second driving motor 3 is sleeved on the hollow transmission shaft Z6 in an empty mode, a motor shaft of the second driving motor 3 is connected with a hollow shaft Z7, and a first gear G1 is fixed on the circumference of the hollow shaft Z7;
a second gear G2 is circumferentially fixed on the hollow transmission shaft Z6, a third gear G3 is arranged on the transmission main shaft Z2 in an empty sleeve mode, and a first synchronizer T1 is arranged between the second gear G2 and the third gear G3 and is circumferentially fixed on the transmission main shaft Z2;
a fourth gear G4 is arranged on the output shaft Z5 in an empty sleeve mode, a third synchronizer T3 is arranged 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 a 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 auxiliary shaft Z3, a tenth gear G10 is arranged on the transmission auxiliary shaft Z3 in an empty sleeve manner, a seventh gear G7 and an eighth gear G8 are circumferentially fixed on the hollow transmission auxiliary shaft Z4, a ninth gear G9 and a twelfth gear G12 are arranged on the hollow transmission auxiliary shaft Z4 in an empty sleeve manner, a fourth synchronizer T4 is arranged between the ninth gear G9 and the twelfth gear G12, a second synchronizer T2 is arranged between the tenth gear G10 and the twelfth gear G12, the second synchronizer T2 is circumferentially fixed on the transmission auxiliary shaft Z3, and a left gear ring of the second synchronizer T2 is circumferentially fixed on a hollow transmission auxiliary shaft Z4;
the front axle transmission shaft Z8 is connected with the transmission auxiliary shaft Z3 through a front axle first gear pair, and the front axle transmission shaft Z8 is connected with the hollow transmission auxiliary shaft Z4 through a front axle second gear pair;
the front axle first gear pair is formed by meshing a sixth gear G6 and a thirteenth gear G13, and the front axle second gear pair is formed by meshing a seventh gear G7 and a fourteenth gear G14;
the sixth gear G6 is meshed with a first gear G1, the seventh gear G7 is meshed with a second gear G2, the third gear G3 is meshed with an eighth gear G8, the fourth gear G4 is meshed with a ninth gear G9, the fifth gear G5 is meshed with a tenth gear G10, and the eleventh gear G11 is meshed with a twelfth gear G12.
In embodiment 1, the thirteenth gear G13 and the fourteenth gear G14 are both disposed on the front axle transmission shaft Z8 in an empty manner, 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.
In embodiment 2, the thirteenth gear G13 and the fourteenth gear G14 are connected with the front axle transmission shaft Z8 through a second planetary gear mechanism, the sun gear shaft Xz of the second planetary gear mechanism forms a sliding fit with the front axle transmission 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 transmission shaft Z8 and the sun gear shaft Xz of the second planetary gear mechanism are both located on the same axial line, the thirteenth gear G13 is fixedly connected with the ring gear Xc of the second planetary gear mechanism, the planet 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 planet gear Xb of the second planetary gear mechanism is connected with the front axle transmission shaft Z8 through the planet carrier Xd of the second planetary gear mechanism, and the planet carrier Xd of the second planetary gear mechanism is fixed on the front axle transmission shaft Z8 in the circumferential direction, the fourteenth gear G14 is circumferentially fixed to the sun gear shaft Xz of the second planetary gear mechanism.
In embodiment 4, the carrier Xd of the second planetary gear set is connected to the front axle transmission shaft Z8 through the second brake B2, and the second brake B2 is used to control the power interruption between the second planetary gear set and the front axle transmission shaft Z8.
For example, with the solution of embodiment 1, the operation mode of the hybrid vehicle is as follows:
engine only mode:
the power of the engine 1 can realize the driving gears of a plurality of gears and realize the function of the AMT automatic transmission by the mutual matching 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 and the like.
A four-wheel drive mode: the rear driving force is output with a fixed torque ratio. The front driving power can realize the power output of a fixed torque ratio when the second synchronizer T2 and the fifth synchronizer T5 are in a gear; when the second synchronizer T2 and the fifth synchronizer T5 are out of gear, the forward drive cannot output power.
Pure electric mode:
the power of the first driving motor 2 is mutually matched through a first synchronizer T1, a second synchronizer T2, a third synchronizer T3 and a fourth synchronizer T4, a plurality of pure electric driving gears can be realized, and gear selection can be carried out according to requirements such as motor states in the driving process. The power of the second driving motor 3 is mutually matched through the first synchronizer T1, the second synchronizer T2, the third synchronizer T3 and the fourth synchronizer T4, a plurality of pure electric driving gears can be realized, and gear selection can be carried out according to requirements such as motor states in the driving process.
A four-wheel drive mode: the rear driving force is output in a fixed torque ratio; when the fifth synchronizer T5 is in gear, the front driving power can be adjusted by a driving motor according to the requirements of front wheels to realize power output with different torque ratios; when the fifth synchronizer T5 is not in gear, the forward drive cannot output power.
Hybrid drive mode:
the engine 1, first driving motor 2, the power of second driving motor 3 passes through clutch C1 jointly, stopper B1, first synchronizer T1, second synchronizer T2, third synchronizer T3, fourth synchronizer T4 mutually supports, can realize a plurality of fuel drive gears and a plurality of electricelectric drive gears, in the drive process, first driving motor 2, the power of second driving motor 3 all can assist the power of engine 1 to realize unpowered interruption and shift, when power is more sufficient, better travelling comfort and smoothness have.
A four-wheel drive mode: the rear driving force is output in a fixed torque ratio; when the fifth synchronizer T5 is in gear, the front driving power can be adjusted by a driving motor according to the requirements of front wheels and is matched with the engine to realize power output with different torque ratios; when the fifth synchronizer T5 is not in gear, the forward drive cannot output power.
An idle mode:
through mutual cooperation of the clutch C1, the brake B1, the first synchronizer T1 and the second synchronizer T2, selection of a plurality of idle speed power generation gears can be achieved, and power of the engine can respectively generate power for the first driving motor 2 and the second driving motor 3 through different gear speed ratios.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and modifications of the present invention by those skilled in the art are within the scope of the present invention without departing from the spirit of the present invention.
Claims (5)
1. A double-motor planetary hybrid power transmission device for a four-wheel drive motor vehicle is characterized by comprising an engine (1), a first drive motor (2) and a second drive motor (3), wherein a gear ring (X3) of a first planetary gear mechanism is fixedly arranged in a rotor of the first drive motor (2) and is connected with a hollow transmission shaft (Z6), a transmission main shaft (Z2) penetrates through the hollow transmission shaft (Z6) to form a concentric shaft and forms a sliding fit with the hollow transmission shaft (Z6), a crankshaft of the engine (1) is connected with a 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 with the transmission main shaft (Z2) through a clutch (C1), and a driving friction component of the clutch (C1) is connected with the planet carrier (X4) of the first planetary gear mechanism, the driven friction assembly is connected with a transmission main shaft (Z2), the planet gear (X2) of the first planetary gear mechanism is arranged between a gear ring (X3) of the first planetary gear mechanism and a sun gear (X1) of the first planetary gear mechanism, a sun gear shaft (X6) of the first planetary gear mechanism is sleeved on an input shaft (Z1) to form a concentric shaft, a sun gear shaft (X6) of the first planetary gear mechanism is connected with a first brake (B1), a driving friction assembly of the first brake (B1) is fixed in a planetary hybrid power transmission box, the driven friction assembly is connected with a sun gear shaft (X6) of the first planetary gear mechanism, an output shaft (Z5) is positioned on the same axial line with the input shaft (Z1) and the transmission main shaft (Z2), the output shaft (Z5) is connected with a rear axle (4) of the four-wheel drive motor vehicle, and the transmission auxiliary shaft (Z3), The front axle transmission shafts (Z8) are all arranged in parallel with the output shaft (Z5), the front axle transmission shafts (Z8) are connected with a front axle (5) of the four-wheel drive motor vehicle, and the transmission auxiliary shaft (Z3) penetrates through a hollow transmission auxiliary shaft (Z4) to form a concentric shaft and forms sliding fit with the hollow transmission auxiliary shaft (Z4);
the rotor of the second driving motor (3) is sleeved on the hollow transmission shaft (Z6) in an empty mode, a motor shaft of the second driving motor (3) is connected with a hollow shaft (Z7), and a first gear (G1) is fixed on the periphery of the hollow shaft (Z7);
a second gear (G2) is circumferentially fixed on the hollow transmission shaft (Z6), a third gear (G3) is arranged on the transmission main shaft (Z2) in an empty sleeve mode, and a first synchronizer (T1) is arranged between the second gear (G2) and the third gear (G3) and is circumferentially fixed on the transmission main shaft (Z2);
a fourth gear (G4) is arranged on the output shaft (Z5) in an empty sleeve mode, a third synchronizer (T3) is arranged 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 a 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 auxiliary shaft (Z3), a tenth gear (G10) is arranged on the transmission auxiliary shaft (Z3) in a hollow manner, a seventh gear (G7) and an eighth gear (G8) are circumferentially fixed on the hollow transmission auxiliary shaft (Z4), a ninth gear (G9) and a twelfth gear (G12) are arranged on the hollow transmission auxiliary shaft (Z4) in a hollow manner, a fourth synchronizer (T4) is arranged between the ninth gear (G9) and the twelfth gear (G12), a second synchronizer (T2) is arranged between the tenth gear (G10) and the twelfth gear (G12), the second synchronizer (T2) is circumferentially fixed on the transmission auxiliary shaft (Z3), and a left gear ring of the second synchronizer (T2) is circumferentially fixed on the hollow transmission auxiliary shaft (Z4);
the front axle transmission shaft (Z8) is connected with the transmission auxiliary shaft (Z3) through a front axle first-gear pair, and the front axle transmission shaft (Z8) is connected with the hollow transmission auxiliary shaft (Z4) through a front axle second-gear pair;
the front axle first gear pair is formed by meshing a sixth gear (G6) and a thirteenth gear (G13), and the front axle second gear pair is formed by meshing a seventh gear (G7) and a fourteenth gear (G14);
the sixth gear (G6) is engaged with a first gear (G1), the seventh gear (G7) is engaged with a second gear (G2), the third gear (G3) is engaged with an eighth gear (G8), the fourth gear (G4) is engaged with a ninth gear (G9), the fifth gear (G5) is engaged with a tenth gear (G10), and the eleventh gear (G11) is engaged with a twelfth gear (G12).
2. The dual-motor planetary hybrid transmission of claim 1, wherein: the thirteenth gear (G13) and the fourteenth gear (G14) are both arranged on the front axle transmission shaft (Z8) in an empty sleeve mode, a fifth synchronizer (T5) is arranged between the thirteenth gear (G13) and the fourteenth gear (G14), and the fifth synchronizer (T5) and the front axle transmission shaft (Z8) are circumferentially fixed.
3. The dual-motor planetary hybrid transmission of claim 1, wherein: the thirteenth gear (G13) and the fourteenth gear (G14) are connected with the front axle transmission shaft (Z8) through a second planetary gear mechanism, a sun gear shaft (Xz) of the second planetary gear mechanism forms a sliding fit with the front axle transmission shaft (Z8) through a bearing, the thirteenth gear (G13) forms a sliding fit with a sun gear shaft (Xz) of the second planetary gear mechanism through a bearing, the front axle transmission shaft (Z8) and the sun gear shaft (Xz) of the second planetary gear mechanism are positioned on the same axial line, the thirteenth gear (G13) is fixedly connected with a gear ring (Xc) of the second planetary gear mechanism, a planet gear (Xb) of the second planetary gear mechanism is arranged between the gear ring (Xc) of the second planetary gear mechanism and the sun gear (Xa) of the second planetary gear mechanism, and a planet gear (Xb) of the second planetary gear mechanism is connected with the front axle transmission shaft (Z8) through a planet carrier (Xd) of the second planetary gear mechanism, the planet carrier (Xd) of the second planetary gear mechanism is circumferentially fixed on a front axle transmission shaft (Z8), and the fourteenth gear (G14) is circumferentially fixed on a sun gear shaft (Xz) of the second planetary gear mechanism.
4. The dual-motor planetary hybrid transmission of claim 3, wherein: the planet carrier (Xd) of the second planetary gear mechanism is sleeved on the front axle transmission shaft (Z8) in an empty mode, and the sixth synchronizer (T6) is circumferentially fixed on the front axle transmission shaft (Z8) and used for controlling the power interruption of the second planetary gear mechanism and the front axle transmission shaft (Z8).
5. The dual-motor planetary hybrid transmission of claim 3, wherein: the planet carrier (Xd) of the second planetary gear mechanism is connected with a front axle transmission shaft (Z8) through a second brake (B2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121472402.3U CN215360910U (en) | 2021-06-30 | 2021-06-30 | Dual-motor planetary hybrid power transmission device for four-wheel drive motor vehicle |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121472402.3U CN215360910U (en) | 2021-06-30 | 2021-06-30 | Dual-motor planetary hybrid power transmission device for four-wheel drive motor vehicle |
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| CN215360910U true CN215360910U (en) | 2021-12-31 |
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| CN202121472402.3U Active CN215360910U (en) | 2021-06-30 | 2021-06-30 | Dual-motor planetary hybrid power transmission device for four-wheel drive motor vehicle |
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- 2021-06-30 CN CN202121472402.3U patent/CN215360910U/en active Active
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