CN112224007B - A multi-mode hybrid special transmission - Google Patents
A multi-mode hybrid special transmission Download PDFInfo
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- CN112224007B CN112224007B CN202011156753.3A CN202011156753A CN112224007B CN 112224007 B CN112224007 B CN 112224007B CN 202011156753 A CN202011156753 A CN 202011156753A CN 112224007 B CN112224007 B CN 112224007B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
- B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/44—Series-parallel type
- B60K6/445—Differential gearing distribution type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/48—Parallel type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
- B60K6/54—Transmission for changing ratio
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
- B60K2006/381—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches characterized by driveline brakes
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Hybrid Electric Vehicles (AREA)
- Structure Of Transmissions (AREA)
Abstract
本发明公开了一种多模式混合动力专用变速器，包括输入轴、第一行星齿轮系、第二行星齿轮系、中间轴、差速器、第一离合器、第二离合器、第一制动器和第二制动器；所述输入轴通过限扭减振器与发动机相连；第一行星齿轮系包括太阳轮A、行星轮A、行星架A和齿圈A，行星轮A设于太阳轮A与齿圈A之间，且安装于行星架A上，行星轮A分别与太阳轮A和齿圈A啮合；太阳轮A安装于输入轴上；第二行星齿轮系包括太阳轮B、行星轮B、行星架B和齿圈B。本发明的有益效果为：设置第一离合器、第二离合器、第一制动器和第二制动器，通过改变第一行星齿轮系和第二行星齿轮系的固连模式，以及改变行星齿轮系中静止的元件，在不增设额外齿轮副的情况下实现多种传动比。
The invention discloses a special multi-mode hybrid transmission, comprising an input shaft, a first planetary gear train, a second planetary gear train, an intermediate shaft, a differential, a first clutch, a second clutch, a first brake and a second brake; the input shaft is connected to the engine through a torsion-limiting damper; the first planetary gear train includes a sun gear A, a planetary gear A, a planet carrier A and a ring gear A, and the planetary gear A is arranged on the sun gear A and the ring gear A between and installed on the planet carrier A, the planet gear A meshes with the sun gear A and the ring gear A respectively; the sun gear A is mounted on the input shaft; the second planetary gear train includes the sun gear B, the planet gear B, the planet carrier B and ring gear B. The beneficial effects of the present invention are as follows: by setting the first clutch, the second clutch, the first brake and the second brake, by changing the fixed connection mode of the first planetary gear train and the second planetary gear train, and changing the stationary mode of the planetary gear train components to achieve a variety of gear ratios without adding additional gear pairs.
Description
Technical Field
The invention relates to automobile power equipment, in particular to a multi-mode hybrid power special transmission.
Background
At present, with the rapid development of electrification in the automobile industry and the gradual increase of market share of new energy automobiles, the trend of electrification of a transmission is more and more obvious. The technical lines in the field of hybrid transmissions can be divided into two categories: the hybrid power transmission comprises an additional hybrid power transmission and a special hybrid power transmission, wherein the additional hybrid power transmission is a hybrid power assembly formed by adding one or two electric machines on the basis of a traditional transmission; the special hybrid power transmission essentially realizes the core function by means of electric drive, and electromechanical components are central components of the structure and are indispensable parts. The special hybrid power transmission is a novel configuration which is newly developed according to the power and torque characteristics of an engine and a motor, and compared with an additional hybrid power transmission, the special hybrid power transmission is more compact and miniaturized in structure; meanwhile, the engine can run in an economic rotating speed range under the support of motor driving, and oil consumption is reduced.
The special hybrid power transmission mainly comprises a multi-mode hybrid special transmission and a power split hybrid special transmission. The multi-mode hybrid special transmission adopts a fixed shaft gear, and a fixed single-speed ratio gear or a multi-speed ratio gear is coupled with a clutch or a brake to couple an engine and a motor, so that the engine is in a high-efficiency area, and the emission and the oil consumption are reduced. This configuration is relatively simple in construction and low in cost, but has limited capability of adjusting the engine operating point. The power split type hybrid special transmission adopts a planetary gear mechanism to couple an engine and a motor for stepless regulation, and regulates and optimizes the running range of the engine through the motor, thereby reducing transient working conditions, ensuring that the engine runs in a high-efficiency area, and reducing emission and oil consumption. The structure is compact, and the working point of the engine can be adjusted more flexibly and effectively by utilizing the power splitting advantage of the planetary gear, so that the fuel economy of the engine is improved. At present, hybrid power transmission driving devices are also available, but cannot meet requirements of multiple working conditions at the same time, for example, chinese patent document CN105128647A relates to a multimode hybrid power transmission driving device, in which it is disclosed that three-stage planet gears are adopted in a transmission system to realize power transmission and change of a driving mode. However, the transmission driving device needs to be provided with two motors to realize different driving modes, has a complex structure and cannot realize direct driving of an engine; the selection of the transmission ratio is less, and the requirement of multiple speed ratios under different working conditions cannot be met.
Disclosure of Invention
The invention aims to provide a multi-gear ratio multi-mode hybrid power special transmission aiming at the defects of the prior art.
The technical scheme adopted by the invention is as follows: a multi-mode hybrid dedicated transmission comprises an input shaft, a first planetary gear train, a second planetary gear train, an intermediate shaft, a differential, a first clutch, a second clutch, a first brake and a second brake;
the input shaft is connected with the engine through a torque-limiting shock absorber;
the first planetary gear train comprises a sun gear A, a planet carrier A and a gear ring A, the planet gear A is arranged between the sun gear A and the gear ring A and is arranged on the planet carrier A, and the planet gear A is respectively meshed with the sun gear A and the gear ring A; the sun gear A is arranged on the input shaft and is connected with the input shaft into a whole;
the second planetary gear train comprises a sun gear B, a planet carrier B and a gear ring B, and the planet gear B is arranged between the sun gear B and the gear ring B and is arranged on the planet carrier B; the planet carrier A of the first planetary gear train is connected with the sun gear B; the gear ring B is meshed with a first gear arranged on the intermediate shaft;
a second gear is arranged on the intermediate shaft and meshed with a differential gear, the differential gear is connected with a differential output shaft, and the differential output shaft is connected with wheels;
one end of the first clutch is connected with a planet carrier B of the second planetary gear train, and the other end of the first clutch is connected with the input shaft;
one end of the second clutch is connected with the gear ring A of the first planetary gear train, and the other end of the second clutch is connected with the planet carrier B of the second planetary gear train;
the first brake is connected with a gear ring A of the first planetary gear train;
the second brake is connected to the carrier a of the first planetary gear train.
According to the scheme, the special transmission further comprises a third planetary gear train, a motor, a third clutch and a fourth clutch, wherein the third planetary gear train comprises a planet carrier C, a first sun gear C, a first planet gear C meshed with the first sun gear, a second sun gear C, a second planet gear C meshed with the second sun gear C, a third sun gear C and a third planet gear C meshed with the third sun gear, the planet carrier C is connected with a rotor of the motor into a whole, and the first planet gear C, the second planet gear C and the third planet gear C are all mounted on the planet carrier C; the first sun gear C is fixedly connected with the rack, the second sun gear C is sleeved on the output shaft of the motor in an empty mode, and the third sun gear C is connected with the output shaft of the motor; one end of the third clutch is connected with the input shaft, and the other end of the third clutch is connected with the output shaft of the motor; one end of the fourth clutch is connected to the ring gear B of the second planetary gear train, and the other end of the fourth clutch is connected to the second sun gear C of the third planetary gear train.
According to the scheme, the multi-mode hybrid power special transmission is in an engine direct drive mode, when the engine directly drives a first gear, the second clutch C is connected, the first brake B is connected, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear a → planet carrier a → sun gear B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel; when the engine directly drives the second gear, the second clutch C is engaged, the second brake B is engaged, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear a → planet gear a → ring gear a → planet carrier B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel; when the engine directly drives the third gear, the first clutch C is engaged, the second clutch C is engaged, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear → planet carrier B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel; when the engine directly drives the fourth gear, the first clutch C is engaged, the second brake B is engaged, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear a → planet carrier B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel; when the engine directly drives the fifth gear, the first clutch C is engaged, the first brake B is engaged, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear a → planet carrier a → sun gear B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel.
According to the scheme, when the multi-mode hybrid power special transmission is in the pure electric drive mode, the fourth clutch is engaged, and the power transmission path is as follows: the power from the motor passes through the carrier C → the second planetary gear C → the second sun gear C → the ring gear B → the first gear on the intermediate shaft → the second gear on the intermediate shaft → the differential gear → the differential output shaft → the wheel.
According to the scheme, when the multi-mode hybrid power special transmission is in the parallel driving mode, the engine is in the direct driving mode by controlling the connection or disconnection of the first clutch, the second clutch, the first brake and the second brake; simultaneously with the engagement of the fourth clutch, the motor drives the wheels, and power from the motor passes through the carrier C → the second planetary gear C → the second sun gear C → the ring gear B → the first gear on the intermediate shaft → the second gear on the intermediate shaft → the differential gear → the differential output shaft → the wheels.
According to the scheme, when the multi-mode hybrid power special transmission is in the power generation mode, the engine is in the direct drive mode and the third clutch or the fourth clutch is engaged at the same time by controlling the engagement or non-engagement of the first clutch, the second clutch, the first brake and the second brake.
According to the scheme, when the multi-mode hybrid special transmission is in the power generation mode, the fourth clutch is engaged, and the engine directly drives the power of any one of the first gear to the fifth gear to the gear ring B → the second sun gear C → the second planet gear C → the planet carrier C → the motor; the third clutch is engaged, and power from the engine passes through the torque limiter damper → sun gear a → third sun gear C on the output shaft of the motor → third planet gear C → carrier C → motor; the third clutch is engaged in the parking power generation mode, and the power transmission path is as follows: the power from the engine passes through the torque limiter damper → the input shaft → the motor output shaft → the third sun gear C on the motor output shaft → the third planet gear C → the carrier C → the motor.
According to the scheme, when the multi-mode hybrid power special transmission is in the braking energy recovery mode, the fourth clutch is engaged, and the power transmission path is as follows: wheel → differential output shaft → differential gear → second gear on the intermediate shaft → first gear on the intermediate shaft → ring gear B → second sun gear C → second planet gear C → carrier C → electric machine.
The invention has the beneficial effects that:
1. the first clutch, the second clutch, the first brake and the second brake are arranged, and 5 transmission ratios can be realized by utilizing two stages of planetary gear trains without additionally arranging an additional gear pair by changing the fixedly connected mode of the first planetary gear train and the second planetary gear train and changing static elements in the planetary gear trains.
2. Through controlling the third clutch and the fourth clutch, the switching of the configurations of the motors P2/P3 is realized, multiple driving modes can be realized under the condition that only one motor is arranged, the power decoupling of the motors and the engine can also be realized, and then the direct driving of the engine is realized. The structure is simple to control and easy to realize, the advantages of both P2 and P3 configurations are fully exerted, the motor can be connected with the engine in parallel when P2 is adopted, and the large-torque driving of the wheels is realized through the speed reduction and torque increase of the planetary gear train; the motor can drive wheels efficiently (pure electric drive mode) at P3, energy loss is small, and braking energy is recovered efficiently (braking energy recovery mode).
3. Through sun gear C and third clutch and the fourth clutch that sets up the axle sleeve structure, realize 6 kinds of drive ratios of driving electricity generation under the prerequisite that need not additionally to increase the gear pair, compact structure and generating efficiency are higher, have improved the economic nature of fuel.
4. In the gear shifting process, a motor can be used for compensating torque or regulating speed, the rotating speed difference of the input end and the output end of the clutch or the brake is reduced to a minimum range, the gear shifting impact can be reduced, the gear shifting is smooth, and the technical requirements and the cost on elements of the clutch and the brake are reduced.
5. The whole structure is compact in structure, the arrangement of the whole vehicle cabin is more facilitated, and the carrying performance advantage is obvious.
Drawings
Fig. 1 is a schematic structural diagram of an embodiment of the present invention.
Wherein; 1. a sun gear A; 2. a planet carrier A; 3. a planet wheel A; 4. a gear ring A; 5. a sun gear B; 6. a planet wheel B; 7. a planet carrier B; 8. a gear ring B; 9. a first sun gear C; 10. a second sun gear C; 11. a third sun gear C; 12. a first planet wheel C; 13. a second planet wheel C; 14. a third planet wheel C; 15. a planet carrier C; 16. a second gear; 17. a first gear; 18. a differential gear; 19. a torsion limiting damper; 20. an input shaft; 30. an output shaft of the motor; 50. and a differential output shaft. B1, a first brake; b2, a second brake; c1, a first clutch; a second clutch of C2; c3, third clutch; c4 and a fourth clutch.
Detailed Description
For a better understanding of the present invention, reference is made to the following detailed description taken in conjunction with the accompanying drawings.
A multi-mode hybrid special transmission as shown in fig. 1, comprising an input shaft 20, a first planetary gear train, a second planetary gear train, an intermediate shaft, a differential, a first clutch C1, a second clutch C2, a first brake B1 and a second brake B2;
the input shaft 20 is connected with an engine through a torque limiting damper 19;
the first planetary gear train comprises a sun gear A1, a planet gear A3, a planet carrier A2 and a gear ring A4, the planet gear A3 is arranged between a sun gear A1 and a gear ring A4 and is mounted on a planet carrier A2, and the planet gear A3 is meshed with a sun gear A1 and a gear ring A4 respectively; the sun gear A1 is arranged on the input shaft 20 and is connected with the input shaft 20 into a whole;
the second planetary gear train comprises a sun gear B5, a planet gear B6, a planet carrier B7 and a gear ring B8, wherein the planet gear B6 is arranged between a sun gear B5 and a gear ring B8 and is mounted on a planet carrier B7; the planet carrier a2 of the first planetary gear train is connected with the sun gear B5; the gear ring B8 is meshed with a first gear 17 arranged on the intermediate shaft;
a second gear 16 is arranged on the intermediate shaft, the second gear 16 is meshed with a differential gear 18, the differential gear 18 is connected with a differential output shaft 50, and the differential output shaft 50 is connected with wheels;
one end of the first clutch C1 is connected with the planet carrier B7 of the second planetary gear train, and the other end of the first clutch C1 is connected with the input shaft 20;
one end of the second clutch C2 is connected with the ring gear A4 of the first planetary gear train, and the other end of the second clutch C2 is connected with the planet carrier B7 of the second planetary gear train;
the first brake B1 is connected with the ring gear A4 of the first planetary gear system;
the second brake B2 is connected to the carrier a2 of the first planetary gear train.
Preferably, the special transmission further comprises a third planetary gear train, an electric motor, a third clutch C3 and a fourth clutch C4, wherein the third planetary gear train comprises a planet carrier C15, a first sun gear C9, a first planet gear C12 engaged with the first sun gear, a second sun gear C10, a second planet gear C13 engaged with the second sun gear C10, a third sun gear C11 and a third planet gear C14 engaged with the third sun gear, the planet carrier C15 is connected with the rotor of the electric motor into a whole, and the first planet gear C12, the second planet gear C13 and the third planet gear C14 are all mounted on the planet carrier C15; the first sun gear C9 is fixedly connected with the frame, the second sun gear C10 is sleeved on the motor output shaft 30 in an empty way, and the third sun gear C11 is connected with the motor output shaft 30; one end of the third clutch C3 is connected with the input shaft 20, and the other end of the third clutch C3 is connected with the motor output shaft 30; one end of the fourth clutch C4 is connected to the ring gear B8 of the second planetary gear train, and the other end of the fourth clutch C4 is connected to the second sun gear C10 of the third planetary gear train.
The special hybrid power transmission can realize a direct engine driving mode, a pure electric driving mode, a parallel driving mode, a power generation mode (driving power generation and parking power generation) and a braking energy recovery mode with 5 forward gears. The states of the clutches and brakes are different in different modes.
1. The multi-mode hybrid power special transmission is in an engine direct drive mode, when the engine directly drives a first gear, the second clutch C2 is engaged, and the first brake B1 is engaged; when the engine directly drives the second gear, the second clutch C2 is engaged, and the second brake B2 is engaged; when the engine directly drives the third gear, the first clutch C1 is engaged, and the second clutch C2 is engaged; when the engine directly drives the fourth gear, the first clutch C1 is engaged, and the second brake B2 is engaged; when the engine directly drives the fifth gear, the first clutch C1 is engaged, and the first brake B1 is engaged. The power transmission paths of all gears in the engine direct drive mode of 5 forward gears are as follows:
(1) the engine directly drives the first gear: the second clutch C2 is engaged and the first brake B1 is engaged. Power from the engine passes through the torque limiter damper 19 → sun gear a1 → planet gear A3 → planet carrier a2 → sun gear B5 → planet gear B6 → ring gear B8 → first gear 17 on the intermediate shaft → second gear 16 on the intermediate shaft → differential gear 18 → differential output shaft 50 → wheels.
(2) The engine directly drives the second gear: the second clutch C2 is engaged and the second brake B2 is engaged. Power from the engine passes through the torque limiter damper 19 → sun gear a1 → planet gear A3 → ring gear a4 → carrier B7 → planet gear B6 → ring gear B8 → first gear 17 on the countershaft → second gear 16 on the countershaft → differential gear 18 → differential output shaft 50 → wheels.
(3) The engine directly drives third gear: the first clutch C1 is engaged, the second clutch C2 is engaged, and the sun gear a1 is connected to the ring gear a4 and the carrier B7. Power from the engine passes through the torque limiter damper 19 → sun gear a1 → carrier B7 → planet gear B6 → ring gear B8 → first gear 17 on the intermediate shaft → second gear 16 on the intermediate shaft → differential gear 18 → differential output shaft 50 → wheels.
(4) The engine directly drives the fourth gear: the first clutch C1 is engaged and the second brake B2 is engaged. Power from the engine passes through the torque limiter damper 19 → sun gear a1 → carrier B7 → planet gear B6 → ring gear B8 → first gear 17 on the intermediate shaft → second gear 16 on the intermediate shaft → differential gear 18 → differential output shaft 50 → wheels.
(5) The engine directly drives five gears: the first clutch C1 is engaged and the first brake B1 is engaged. Power from the engine passes through the torque limiter damper 19 → sun gear a1 → planet gear A3 → planet carrier a2 → sun gear B5 → planet gear B6 → ring gear B8 → first gear 17 on the intermediate shaft → second gear 16 on the intermediate shaft → differential gear 18 → differential output shaft 50 → wheels.
2. The fourth clutch C4 is engaged when the multi-mode hybrid-only transmission is in the electric-only drive mode. The power transmission path in this mode is: power from the motor passes through the carrier C15 → the second planet gear C13 → the second sun gear C10 → the ring gear B8 → the first gear 17 on the intermediate shaft → the second gear 16 on the intermediate shaft → the differential gear 18 → the differential output shaft 50 → the wheels.
3. When the multi-mode hybrid transmission is in the parallel driving mode, the engine is in the direct driving mode and the fourth clutch C4 is engaged by controlling the engagement or non-engagement of the first clutch C1, the second clutch C2, the first brake B1 and the second brake B2. The power transmission path in this mode is:
(1) engine-driven wheels: the engine drives any of the five gears for a total of five speed ratios.
(2) The motor drives the wheels: the fourth clutch C4 is engaged. Power from the motor passes through the carrier C15 → the second planet gear C13 → the second sun gear C10 → the ring gear B8 → the first gear 17 on the intermediate shaft → the second gear 16 on the intermediate shaft → the differential gear 18 → the differential output shaft 50 → the wheels.
4. When the special multi-mode hybrid power transmission is in a power generation mode, (1) driving power generation: the engine is placed in the direct drive mode by controlling the engagement and disengagement of the first clutch C1, the second clutch C2, the first brake B1 and the second brake B2, and the third clutch C3 or the fourth clutch C4 is engaged, and the power transmission path in the power generation mode is as follows:
1) speed ratio 1-speed ratio 5: the fourth clutch C4 is engaged. Any one of the five direct-drive gears (5 speed ratios) of the engine is adopted, and power is transmitted to the ring gear B8 → the second sun gear C10 → the second planet gear C13 → the planet carrier C15 → the motor.
2) The speed ratio is 6: the third clutch C3 is engaged. The power from the engine passes through the torque limiter damper 19 → the sun gear a1 → the third sun gear C11 on the motor output shaft 30 → the third planet gear C14 → the carrier C15 → the motor.
(2) Parking power generation: the third clutch C3 is engaged, and the power transmission path in the power generation mode is: the power from the engine passes through the torque limiter damper 19 → the input shaft 20 → the motor output shaft 30 → the third sun gear C11 on the motor output shaft 30 → the third planet gear C14 → the carrier C15 → the motor.
5. When the multi-mode hybrid power special transmission is in a braking energy recovery mode, the fourth clutch C4 is engaged, and the power transmission path in the mode is as follows: the fourth clutch C4 is engaged. Wheel → differential output shaft 50 → differential gear 18 → second gear 16 on the intermediate shaft → first gear 17 on the intermediate shaft → ring gear B8 → second sun gear C10 → second planet gear C13 → carrier C15 → electric machine.
It should be noted that the above-mentioned embodiments are only preferred embodiments of the present invention, and the present invention is not limited thereto, and although the present invention has been described in detail with reference to the embodiments, it will be apparent to those skilled in the art that modifications can be made to the technical solutions described in the above-mentioned embodiments, or equivalent substitutions of some technical features, but any modifications, equivalents, improvements and the like within the spirit and principle of the present invention shall be included in the protection scope of the present invention.
Claims (7)
1. A multi-mode hybrid dedicated transmission is characterized by comprising an input shaft, a first planetary gear train, a second planetary gear train, an intermediate shaft, a differential, a first clutch, a second clutch, a first brake and a second brake;
the input shaft is connected with the engine through a torque-limiting shock absorber;
the first planetary gear train comprises a sun gear A, a planet carrier A and a gear ring A, the planet gear A is arranged between the sun gear A and the gear ring A and is arranged on the planet carrier A, and the planet gear A is respectively meshed with the sun gear A and the gear ring A; the sun gear A is arranged on the input shaft and is connected with the input shaft into a whole;
the second planetary gear train comprises a sun gear B, a planet carrier B and a gear ring B, and the planet gear B is arranged between the sun gear B and the gear ring B and is arranged on the planet carrier B; the planet carrier A of the first planetary gear train is connected with the sun gear B; the gear ring B is meshed with a first gear arranged on the intermediate shaft;
a second gear is arranged on the intermediate shaft and meshed with a differential gear, the differential gear is connected with a differential output shaft, and the differential output shaft is connected with wheels;
one end of the first clutch is connected with a planet carrier B of the second planetary gear train, and the other end of the first clutch is connected with the input shaft;
one end of the second clutch is connected with the gear ring A of the first planetary gear train, and the other end of the second clutch is connected with the planet carrier B of the second planetary gear train;
the first brake is connected with a gear ring A of the first planetary gear train;
the second brake is connected with a planet carrier A of the first planetary gear system;
the special transmission also comprises a third planetary gear train, a motor, a third clutch and a fourth clutch, wherein the third planetary gear train comprises a planet carrier C, a first sun gear C, a first planet gear C meshed with the first sun gear, a second sun gear C, a second planet gear C meshed with the second sun gear C, a third sun gear C and a third planet gear C meshed with the third sun gear C, the planet carrier C is connected with a rotor of the motor into a whole, and the first planet gear C, the second planet gear C and the third planet gear C are all mounted on the planet carrier C; the first sun gear C is fixedly connected with the rack, the second sun gear C is sleeved on the output shaft of the motor in an empty mode, and the third sun gear C is connected with the output shaft of the motor; one end of the third clutch is connected with the input shaft, and the other end of the third clutch is connected with the output shaft of the motor; one end of the fourth clutch is connected to the ring gear B of the second planetary gear train, and the other end of the fourth clutch is connected to the second sun gear C of the third planetary gear train.
2. The multi-mode hybrid dedicated transmission of claim 1, wherein the multi-mode hybrid dedicated transmission is in an engine direct drive mode, the second clutch is engaged and the first brake is engaged when the engine is directly driving first gear, and the power transmission path is: power from the engine passes through the torque limiter damper → sun gear a → planet carrier a → sun gear B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel; when the engine directly drives the second gear, the second clutch is engaged, the second brake is engaged, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear a → planet gear a → ring gear a → planet carrier B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel; when the engine directly drives the third gear, the first clutch is engaged, the second clutch is engaged, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear → planet carrier B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel; when the engine directly drives the fourth gear, the first clutch is engaged, the second brake is engaged, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear a → planet carrier B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel; when the engine directly drives the fifth gear, the first clutch is engaged, the first brake is engaged, and the power transmission path is as follows: power from the engine passes through the torque limiter damper → sun gear a → planet carrier a → sun gear B → planet gear B → ring gear B → first gear on the intermediate shaft → second gear on the intermediate shaft → differential gear → differential output shaft → wheel.
3. The multi-mode hybrid dedicated transmission of claim 1, wherein when the multi-mode hybrid dedicated transmission is in the electric only drive mode, the fourth clutch is engaged and the power transmission path is: the power from the motor passes through the carrier C → the second planetary gear C → the second sun gear C → the ring gear B → the first gear on the intermediate shaft → the second gear on the intermediate shaft → the differential gear → the differential output shaft → the wheel.
4. The multi-mode hybrid dedicated transmission of claim 2, wherein the engine is placed in a direct drive mode by controlling the engagement or non-engagement of the first clutch, the second clutch, the first brake, and the second brake when the multi-mode hybrid dedicated transmission is placed in a parallel drive mode; simultaneously with the engagement of the fourth clutch, the motor drives the wheels, and power from the motor passes through the carrier C → the second planetary gear C → the second sun gear C → the ring gear B → the first gear on the intermediate shaft → the second gear on the intermediate shaft → the differential gear → the differential output shaft → the wheels.
5. A multi-mode hybrid dedicated transmission as set forth in claim 2, wherein the engine is placed in a direct drive mode while the third clutch or the fourth clutch is engaged by controlling whether the first clutch, the second clutch, the first brake, and the second brake are engaged or not when the multi-mode hybrid dedicated transmission is placed in a generating mode.
6. The multi-mode hybrid specific transmission of claim 5, wherein when the multi-mode hybrid specific transmission is in the drive generating mode, the fourth clutch is engaged, the engine directly drives power from first to fifth gears to the ring gear B → the second sun gear C → the second planet gear C → the carrier C → the electric machine, or the third clutch is engaged, power from the engine passes through the torque limiter damper → sun gear A → the third sun gear C on the output shaft of the electric machine → the third planet gear C → the carrier C → the electric machine; the third clutch is engaged in the parking power generation mode, and the power transmission path is as follows: the power from the engine passes through the torque limiter damper → the input shaft → the motor output shaft → the third sun gear C on the motor output shaft → the third planet gear C → the carrier C → the motor.
7. The multi-mode hybrid dedicated transmission of claim 1, wherein when the multi-mode hybrid dedicated transmission is in a braking energy recovery mode, the fourth clutch is engaged and the power transmission path is: wheel → differential output shaft → differential gear → second gear on the intermediate shaft → first gear on the intermediate shaft → ring gear B → second sun gear C → second planet gear C → carrier C → electric machine.
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| CN113071305B (en) * | 2021-04-28 | 2022-05-24 | 青岛科麟智传汽车科技有限公司 | Three-planet-row hybrid power driving device |
| KR102566922B1 (en) * | 2021-04-29 | 2023-08-16 | 현대모비스 주식회사 | Power transmission device and automobile including the same |
| CN115891615A (en) * | 2021-09-30 | 2023-04-04 | 比亚迪股份有限公司 | Hybrid system and vehicle having same |
| CN114274758B (en) * | 2021-12-31 | 2023-05-09 | 东风汽车集团股份有限公司 | A hybrid transmission, a hybrid drive system, and a vehicle |
| CN114801689B (en) * | 2022-03-18 | 2024-10-22 | 凯博易控车辆科技(苏州)股份有限公司 | A hybrid power system |
| CN118790030B (en) * | 2024-08-05 | 2025-10-31 | 奇瑞汽车股份有限公司 | Hybrid power system and vehicle |
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