Dual-motor planetary hybrid transmission for motor vehicles

Abstract

A dual-motor planetary hybrid power transmission device for a motor vehicle, a ring gear of a planetary gear mechanism is fixedly arranged in the 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, the crankshaft of the engine is connected to the planetary carrier of the planetary gear mechanism through an input shaft, the planetary carrier is connected to the transmission main shaft through a clutch, the sun gear shaft is connected to a brake, the active friction component of the brake is fixed in the housing of the planetary hybrid power transmission device, the driven friction component is connected to the sun gear shaft, an output shaft and the input shaft and the transmission main shaft are all located on the same axis line, a transmission countershaft is arranged parallel to the output shaft, the transmission countershaft passes through a hollow transmission countershaft to form a coaxial shaft, and forms a sliding fit with the hollow transmission countershaft; the rotor of the second drive motor is loosely sleeved on the hollow transmission shaft, the motor shaft of the second drive motor is connected to a hollow shaft, and the hollow shaft circumferentially fixes the first gear.

Description

Technical Field

[0001] The invention relates to the field of hybrid power vehicles, and in particular to a dual-motor planetary hybrid power transmission device for a 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 Electric Drive Device" with publication number CN108944405A provides a hybrid electric drive device, including: an engine, a first motor, a second motor, a split speed change mechanism and a drive speed change mechanism; the split speed change mechanism includes a first planetary row, a second planetary row, a first shift clutch element, and a second shift clutch element. The first planetary row includes a first sun gear, a first planetary carrier and a first ring gear. The second planetary row includes a second sun gear, a second planetary carrier and a second ring gear. The engine is connected to the first planetary carrier, the first motor is connected to the first sun gear, and the first planetary carrier is connected to the second sun gear; the drive speed change mechanism includes a third planetary row, a third shift brake element and a fourth shift brake element. The power of the second motor passes through the drive speed change mechanism and then merges with the power output by the second planetary carrier to output and drive the vehicle. The gear is switched by the split speed change mechanism and the drive speed change mechanism, thereby improving the performance of the hybrid electric drive device. However, this mechanism requires multiple clutches and multiple planetary mechanism groups to cooperate with each other to achieve the power transmission function of different gears. It has a complex structure and can only achieve a small number of drive gears, which is not conducive to the economical power distribution of the car and cannot meet the needs of the car in a variety of driving conditions and driving environments. 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 motor vehicle, which adopts two small and low-cost motors to share power according to the working conditions of the vehicle, and utilizes a planetary gear mechanism and a gear transmission mechanism to form a multi-speed transmission mechanism to distribute the power of the engine and the drive motor, thereby increasing the number of pure electric drive gears and fuel drive gears. It is used for vehicles with rich functional and environmental requirements, can more effectively optimize fuel economy, and is conducive to 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 motor vehicle, comprising an engine, a first drive motor, a second drive motor, a planetary gear mechanism with a ring gear fixedly arranged in the 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 slides with the hollow transmission shaft through a bearing, the crankshaft of the engine is connected to the planet carrier of the planetary gear mechanism through an input shaft, the planet carrier is connected to the transmission main shaft through a clutch, and the active friction component of the clutch is connected to the planet carrier Then, the driven friction assembly is connected to the transmission main shaft, the planetary gear of the planetary gear mechanism is arranged between the ring gear and the sun gear, the sun gear shaft of the sun gear is sleeved on the input shaft to form a concentric shaft, the sun gear shaft is connected to a brake, the active friction assembly of the brake is fixed in the housing of the planetary hybrid power transmission device, the driven friction assembly is connected to the sun gear shaft, an output shaft and the input shaft and the transmission main shaft are all located on the same axis line, a transmission countershaft is arranged in parallel with the output shaft, 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 hollow transmission countershaft is circumferentially fixed with a seventh gear and an eighth gear, the eighth gear is meshed with the third gear to form a first gear pair, and the seventh gear is meshed with the second gear;

[0010] The hollow transmission countershaft is connected to the output shaft via a transmission gear pair, a third synchronizer is arranged between the first gear pair and the transmission gear pair and is circumferentially fixed on the output shaft, and the left gear ring of the third synchronizer is circumferentially fixed on the transmission main shaft;

[0011] The idle sleeve of the transmission countershaft is provided with a tenth gear, a second synchronizer is provided between the transmission gear pair and the tenth gear and is circumferentially fixed on the transmission countershaft, and the left gear ring of the second synchronizer is circumferentially fixed on the hollow transmission countershaft;

[0012] A fifth gear is fixed circumferentially on the output shaft, and the fifth gear is meshed with the tenth gear. A sixth gear is fixed circumferentially on the transmission countershaft, and the sixth gear is meshed with the first gear.

[0013] Preferably, the transmission gear pair is a second gear pair, the second gear pair is composed of a fourth gear meshing with a ninth gear, the fourth gear is loosely mounted on the output shaft, and the ninth gear is circumferentially fixed on a hollow transmission secondary shaft.

[0014] Preferably, the transmission gear pair consists of a second gear pair and a third gear pair, the second gear pair consists of a fourth gear meshing with a ninth gear, the third gear pair consists of an eleventh gear meshing with a twelfth gear, the fourth gear is loosely mounted on the output shaft, the eleventh gear is circumferentially fixed on the output shaft, the ninth gear and the twelfth gear are both loosely mounted on a hollow transmission secondary shaft, and a fourth synchronizer is arranged between the ninth gear and the twelfth gear and is circumferentially fixed on the hollow transmission secondary shaft.

[0015] By adopting the above scheme, the rotor of the second drive motor is loosely mounted on the hollow transmission shaft, the motor shaft of the second drive motor is connected to a hollow shaft, the first gear is circumferentially fixed on the hollow shaft, the sixth gear is circumferentially fixed on the transmission countershaft, the first gear is meshed with the sixth gear, and the power is diverted by using a planetary gear mechanism. The first drive motor and the second drive motor can cooperate with the engine simultaneously or separately to participate in driving the hybrid vehicle, and can cooperate with each other to compensate for power during gear changes.

[0016] The advantages of the present invention are as follows:

[0017] 1. In the technical solution of the present invention, according to the characteristics of the dual-motor drive and multi-speed transmission system, only a drive motor with smaller power and volume is needed to meet the driving requirements of the entire vehicle.

[0018] 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.

[0019] 3. 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;

[0020] 4. 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

[0021] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present invention;

[0022] Figure 2 This is a schematic diagram of the structure of Embodiment 2 of the present invention;

[0023] Figure 3 This is the gear distribution diagram of the present invention. DETAILED DESCRIPTION

[0024] like Figures 1 to 3 As shown, a dual-motor planetary hybrid power transmission device for a motor vehicle includes an engine 1, a first drive motor 2, and a second drive motor 3. A ring gear X3 of a 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 is slidably matched with the hollow transmission shaft Z6 through a bearing. The crankshaft of the engine 1 is connected to the planet carrier X4 of the planetary gear mechanism through an input shaft Z1. The planet carrier X4 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, and the driven friction component is connected to the transmission main shaft Z2. The planetary gear X2 of the planetary gear mechanism is arranged between the ring gear X3 and the sun gear X1, the sun gear shaft X6 of the sun gear X1 is loosely sleeved on the input shaft Z1 to form a coaxial shaft, the sun gear shaft X6 is connected to a brake B1, the active friction component of the 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, an output shaft Z5 is located on the same axis as the input shaft Z1 and the transmission main shaft Z2, a transmission countershaft Z3 is arranged in parallel with the output shaft Z5, 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;

[0025] 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;

[0026] 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;

[0027] The hollow transmission countershaft Z4 is circumferentially fixed with a seventh gear G7 and an eighth gear G8, the eighth gear G8 meshes with the third gear G3 to form a first gear pair, and the seventh gear G7 meshes with the second gear G2;

[0028] The hollow transmission countershaft Z4 is connected to the output shaft Z5 via a transmission gear pair, a third synchronizer T3 is arranged between the first gear pair and the transmission gear pair and is circumferentially fixed on the output shaft Z5, and a left gear ring of the third synchronizer T3 is circumferentially fixed on the transmission main shaft Z2;

[0029] The tenth gear G10 is set in an empty sleeve on the transmission countershaft Z3, and a second synchronizer T2 is set between the transmission gear pair and the tenth gear G10 and is circumferentially fixed on the transmission countershaft Z3, and the left gear ring of the second synchronizer T2 is circumferentially fixed on the hollow transmission countershaft Z4;

[0030] A fifth gear G5 is fixed circumferentially on the output shaft Z5, and the fifth gear G5 is meshed with the tenth gear G10. A sixth gear G6 is fixed circumferentially on the transmission countershaft Z3, and the sixth gear G6 is meshed with the first gear G1.

[0031] In Example 1, the transmission gear pair is the second gear pair, and the second gear pair is composed of a fourth gear G4 meshing with a ninth gear G9. The fourth gear G4 is loosely mounted on the output shaft Z5, and the ninth gear G9 is circumferentially fixed on the hollow transmission secondary shaft Z4.

[0032] In Example 2, the transmission gear pair is composed of a second gear pair and a third gear pair, the second gear pair is composed of a fourth gear G4 meshing with a ninth gear G9, the third gear pair is composed of an eleventh gear G11 meshing with a twelfth gear G12, the fourth gear G4 is loosely mounted on the output shaft Z5, the eleventh gear G11 is circumferentially fixed on the output shaft Z5, the ninth gear G9 and the twelfth gear G12 are both loosely mounted on the hollow transmission countershaft Z4, and a fourth synchronizer T4 is arranged between the ninth gear G9 and the twelfth gear G12 and is circumferentially fixed on the hollow transmission countershaft Z4.

[0033] The operation mode of the hybrid vehicle adopting the above scheme is as follows:

[0034] Engine-only mode:

[0035] The power of the engine 1 cooperates with each other through the clutch C1, the brake B1, the first synchronizer T1, the second synchronizer T2, and the third synchronizer T3 to achieve 9 driving gears including a direct drive gear, thereby realizing the AMT automatic transmission function.

[0036] Pure electric mode:

[0037] The power of the driving motor 1 cooperates with each other through the first synchronizer T1, the second synchronizer T2, the third synchronizer T3, and the fourth synchronizer T4 to achieve 4 pure electric driving gears. The gear can be selected according to the motor status and other requirements during the driving process.

[0038] The power of the driving motor 2 cooperates with each other through the first synchronizer T1, the second synchronizer T2, the third synchronizer T3, and the fourth synchronizer T4 to achieve 5 pure electric driving gears. The gear can be selected according to the motor status and other requirements during the driving process.

[0039] Hybrid drive mode:

[0040] 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 9 fuel drive gears including a direct drive gear and 4+5 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.

[0041] Idle mode:

[0042] Through the cooperation of the clutch C1, the brake B1, the first synchronizer T1 and the second synchronizer T2, five 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 five idle gears.

[0043] 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 motor 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 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 is slidably matched with the hollow transmission shaft (Z6) via a bearing; the crankshaft of the engine (1) is connected to the planet carrier (X4) of the planetary gear mechanism via an input shaft (Z1); the planet carrier (X4) is connected to the transmission main shaft (Z2) via a clutch (C1); the active friction component of the clutch (C1) is connected to the planet carrier (X4); the driven friction component is connected to the transmission main shaft (Z2); the planetary gear mechanism is connected to the planet carrier (X4); the driven friction component is connected to the transmission main shaft (Z2); The planetary gear (X2) of the gear mechanism is arranged between the ring gear (X3) and the sun gear (X1); the sun gear shaft (X6) of the sun gear (X1) is loosely sleeved on the input shaft (Z1) to form a coaxial shaft; the sun gear shaft (X6) is connected to a brake (B1); the active friction component of the 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); an output shaft (Z5) and the input shaft (Z1) and the transmission main shaft (Z2) are all located on the same axis; a transmission secondary shaft (Z3) is arranged in parallel with the output shaft (Z5); the transmission secondary shaft (Z3) passes through a hollow transmission secondary shaft (Z4) to form a coaxial shaft and forms a sliding fit with the hollow transmission secondary shaft (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); The hollow transmission countershaft (Z4) is circumferentially fixed with a seventh gear (G7) and an eighth gear (G8), the eighth gear (G8) meshes with the third gear (G3) to form a first gear pair, and the seventh gear (G7) meshes with the second gear (G2); The hollow transmission countershaft (Z4) and the output shaft (Z5) are connected via a transmission gear pair, a third synchronizer (T3) is arranged between the first gear pair and the transmission gear pair and is circumferentially fixed on the output shaft (Z5), and a left gear ring of the third synchronizer (T3) is circumferentially fixed on the transmission main shaft (Z2); A tenth gear (G10) is provided in an empty sleeve on the transmission countershaft (Z3); a second synchronizer (T2) is provided between the transmission gear pair and the tenth gear (G10) and 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); A fifth gear (G5) is fixed circumferentially on the output shaft (Z5), and the fifth gear (G5) is meshed with the tenth gear (G10). A sixth gear (G6) is fixed circumferentially on the transmission countershaft (Z3), and the sixth gear (G6) is meshed with the first gear (G1).

2. The dual-motor planetary hybrid power transmission device according to claim 1, characterized in that: The transmission gear pair is a second gear pair, which is composed of a fourth gear (G4) meshing with a ninth gear (G9), the fourth gear (G4) is loosely sleeved on the output shaft (Z5), and the ninth gear (G9) is circumferentially fixed on the hollow transmission secondary shaft (Z4).

3. The dual-motor planetary hybrid power transmission device according to claim 1, characterized in that: The transmission gear pair is composed of a second gear pair and a third gear pair. The second gear pair is composed of a fourth gear (G4) meshing with a ninth gear (G9). The third gear pair is composed of an eleventh gear (G11) meshing with a twelfth gear (G12). The fourth gear (G4) is loosely sleeved on an output shaft (Z5). The eleventh gear (G11) is circumferentially fixed on the output shaft (Z5). The ninth gear (G9) and the twelfth gear (G12) are both loosely sleeved on a hollow transmission countershaft (Z4). A fourth synchronizer (T4) is arranged between the ninth gear (G9) and the twelfth gear (G12) and is circumferentially fixed on the hollow transmission countershaft (Z4).

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