CN108583273B - Integrated two-gear variable-speed electric drive bridge with electronic parking function - Google Patents
Integrated two-gear variable-speed electric drive bridge with electronic parking function Download PDFInfo
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- CN108583273B CN108583273B CN201810255809.7A CN201810255809A CN108583273B CN 108583273 B CN108583273 B CN 108583273B CN 201810255809 A CN201810255809 A CN 201810255809A CN 108583273 B CN108583273 B CN 108583273B
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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
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
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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
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/10—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of fluid gearing
- B60K17/105—Units comprising at least a part of the gearing and a torque-transmitting axle, e.g. transaxles
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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
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
- B60K17/165—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing provided between independent half axles
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
- Structure Of Transmissions (AREA)
- Braking Arrangements (AREA)
Abstract
The invention discloses an integrated two-gear speed change electric drive bridge with an electronic parking function, which comprises a transmission system and a hydraulic system, wherein the transmission system comprises a transmission shaft, a transmission shaft and a transmission shaft; the invention integrates the original driving motor, the clutch, the two-gear transmission, the transmission shaft and the drive axle, can eliminate the need of the clutch, the transmission shaft and the main reducer of the drive axle, replaces the clutch with an elastic coupling, adopts a plurality of wet clutches to cooperate with an automatic gear shifting program to carry out automatic gear shifting and an active lubricating system, and changes a left manual parking brake and a right manual parking brake in wheels and parking brakes into an electronic central wet parking brake on the transmission, thereby reducing the weight, lowering the production and maintenance cost and improving the transmission efficiency.
Description
Technical Field
The invention relates to an integrated two-gear speed change electric drive axle with an electronic parking function.
Background
In the two-gear electric passenger vehicles, electric sanitation vehicles, electric logistics vehicles and other vehicles on the market at present, a two-gear transmission driven by a motor-connected clutch is connected with a universal joint transmission shaft and then connected with a drive axle, and two-wheel parking braking is adopted, as shown in figure 1, a driving motor 1 changes the speed through a clutch 2 and a two-gear transmission 3 to drive a universal joint transmission shaft 4 to rotate, and power is transmitted to wheels 6 through a drive axle 5.
Disclosure of Invention
In order to reduce the weight, improve the endurance mileage and further reduce the cost, the invention provides an integrated two-gear speed change axle with an automatic parking function for an electric vehicle, which can automatically switch between two gears.
The technical scheme adopted by the invention is as follows: an integrated two-gear speed change electric drive bridge with electronic parking comprises a transmission system and a hydraulic system;
the transmission system comprises a central wet-type parking brake, a low-speed gear driving gear, an input shaft, a high-speed gear driving gear, an elastic coupling, a driving motor, a high-speed gear driven gear, a wet-type clutch B, a wet-type clutch A, an intermediate shaft, a low-speed gear driven gear, an intermediate shaft gear, a left half shaft, an output shaft gear, a differential assembly and a right half shaft;
the driving motor transmits torque and rotating speed to the transmission input shaft, the low-gear driving gear and the high-gear driving gear through the elastic coupling, the low-gear driving gear transmits the torque and the rotating speed to the low-gear driven gear, and the high-gear driving gear transmits the torque and the rotating speed to the high-gear driven gear;
the low-gear driven gear and the high-gear driven gear are both arranged on an intermediate shaft, a central wet parking brake is arranged on the intermediate shaft, a wet clutch A and a wet clutch B are respectively meshed with the low-gear driven gear and the high-gear driven gear, and a differential assembly is driven by an intermediate shaft gear to drive a left half shaft and a right half shaft to rotate;
the transmission mechanism also comprises an oil pump motor which provides power for each oil cylinder through a gear oil pump in the hydraulic system;
the hydraulic system comprises a central wet parking brake oil cylinder, a two-position three-way pilot-operated electric proportional pressure reducing valve A, a gear oil pump, a two-position three-way pilot-operated electric proportional pressure reducing valve B, a wet clutch B oil cylinder, a wet clutch A oil cylinder, a two-position three-way electromagnetic valve, a pressure reducing valve and a one-way valve;
the gear oil pump respectively transmits system pressure oil to a wet clutch A oil cylinder, a wet clutch B oil cylinder and a central wet parking brake oil cylinder through a two-position three-way pilot type electric proportional pressure reducing valve A, a two-position three-way pilot type electric proportional pressure reducing valve B and a two-position three-way electromagnetic valve, and residual system pressure oil returns to an oil tank and each lubricating point through a pressure reducing valve and a one-way valve.
Furthermore, a magnetic filter is arranged between an oil tank and the gear oil pump in the hydraulic system; the filter with the pollution indication and the bypass and the temperature sensor are connected in series at the rear part of the gear oil pump; a pilot overflow valve is arranged on a branch at the rear end of the temperature sensor.
The invention has the following beneficial effects: the invention integrates the original driving motor, the clutch, the two-gear transmission, the transmission shaft and the drive axle, can eliminate the need of the main speed reducer of the clutch, the transmission shaft and the drive axle, replaces the clutch with a torsional vibration damper, adopts a plurality of wet clutches to match with an automatic gear shifting program to carry out automatic gear shifting and an active lubricating system, and changes a left manual parking brake and a right manual parking brake in wheels and parking brakes into an electronic central wet parking brake on the transmission, thereby reducing the weight, lowering the production and maintenance cost and improving the transmission efficiency.
Drawings
FIG. 1 is a power diagram of a conventional two-gear passenger car;
FIG. 2 is a schematic diagram of the transmission system of the present invention;
fig. 3 is a schematic diagram of the hydraulic system of the present invention.
In the figure: 1-driving motor, 2-clutch, 3-two-gear speed changer, 4-universal joint transmission shaft, 5-power drive axle and 6-wheel;
101-central wet parking brake, 102-low gear driving gear, 103-input shaft, 104-high gear driving gear, 105-elastic coupling, 107-oil pump motor, 108-driving motor, 109-high gear driven gear, 110-wet clutch B, 111-wet clutch A, 112-intermediate shaft, 113-low gear driven gear, 114-intermediate shaft gear, 115-left half shaft, 116-output shaft gear, 117-differential assembly, 118-right half shaft;
201-central wet parking brake cylinder, 202-magnetic filter, 203-filter with pollution only and bypass, 204-temperature sensor, 205-pilot overflow valve, 206-two-position three-way pilot electric proportional pressure reducing valve A, 207-gear oil pump, 208-two-position three-way pilot electric proportional pressure reducing valve B, 209-oil tank, 210-wet clutch B cylinder, 211-wet clutch A cylinder, 212-two-position three-way electromagnetic valve, 213-pressure reducing valve, 214-cooler with bypass, 215-one-way valve.
Detailed Description
The invention will be further described with reference to the accompanying drawings.
The invention relates to an integrated two-gear speed-changing electric drive axle with electronic parking, which comprises a transmission system and a hydraulic system, wherein the transmission system comprises a central wet parking brake 101, a low-gear driving gear 102, an input shaft 103, a high-gear driving gear 104, an elastic coupling 105, a driving motor 108, a high-gear driven gear 109, a wet clutch B110, a wet clutch A111, an intermediate shaft 112, a low-gear driven gear 113, an intermediate shaft gear 114, a left half shaft 115, an output shaft gear 116, a differential assembly 117 and a right half shaft 118, as shown in figure 2.
The driving motor 108 transmits torque and rotation speed to the transmission input shaft 103, the low-gear driving gear 102 and the high-gear driving gear 104 through the elastic coupling 105, the low-gear driving gear 102 transmits the torque and rotation speed to the low-gear driven gear 113, and the high-gear driving gear 104 transmits the torque and rotation speed to the high-gear driven gear 109; the low-gear driven gear 113 and the high-gear driven gear 109 are both arranged on the intermediate shaft 112, and the intermediate shaft 112 is also provided with a central wet parking brake 101. The wet clutch a111 and the wet clutch B110 are engaged with the low-gear driven gear 113 and the high-gear driven gear 109, respectively, and drive the differential assembly 117 to rotate the left half shaft 115 and the right half shaft 118 by the torque and the rotational speed output shaft gear 116 through the intermediate shaft gear 114.
When the transmission is in the first gear ratio, the wet clutch a111 is engaged, and the low-speed driven gear 13 transmits torque and rotation speed to the countershaft gear 114 through the countershaft 112, and then the countershaft gear 114 transmits the torque and rotation speed to the left half shaft 115 and the right half shaft 118 through the output shaft gear 116 and the differential assembly 117.
When the transmission is in the second gear ratio, the wet clutch B110 is engaged, and the driven gear 109 in the high gear transmits torque and rotational speed to the countershaft gear 114 through the countershaft 112, and then the countershaft gear 114 transmits torque and rotational speed to the left half shaft 115 and the right half shaft 118 through the output shaft gear 116 and the differential assembly 117.
When in neutral, neither wet clutch a111 nor wet clutch B110 is engaged.
When the vehicle is in a parking gear, the pressure of the oil cylinder piston cavity of the central wet parking brake 101 is released by controlling the electromagnetic valve, and the friction plate is pressed tightly under the action of a spring of the central wet parking brake to realize braking; and neither wet clutch a111 nor wet clutch B110 is engaged.
The reverse is achieved by the reverse rotation of the drive motor 108, and the reverse gears are controlled in accordance with the forward control mode.
As shown in fig. 3, the hydraulic system is a system integrating control and active lubrication; the pressure oil source for providing the control and lubrication system is provided by a gear oil pump 207 driven by a constant speed oil pump motor 107 rotating in a single direction, so that the control pressure of the hydraulic system is kept constant.
The hydraulic system includes a central wet parking brake cylinder 201, a magnetic filter 202, a filter 203 with contamination indication and bypass, a temperature sensor 204, a pilot relief valve 205, a two-position three-way pilot type electro-proportional pressure reducing valve a206, a gear oil pump 207, a two-position three-way pilot type electro-proportional pressure reducing valve B208, an oil tank 209, a wet clutch B cylinder 210, a wet clutch a cylinder 211, a two-position three-way solenoid valve 212, a pressure reducing valve 213, a cooler 214 with bypass, and a check valve 215. The gear oil pump 207 pumps out system pressure oil in an oil tank 209, the system pressure oil is filtered by the magnetic filter 202 and then enters the filter 203 with pollution indication and bypass and the temperature sensor 204, and a pilot-operated overflow valve 205 is arranged at the tail end of a branch, and the pilot-operated overflow valve 205 is used for setting the control pressure of the hydraulic system. The gear oil pump 207 conveys system pressure oil to a wet clutch A oil cylinder 211, a wet clutch B oil cylinder 210 and a central wet parking brake oil cylinder 201 through a two-position three-way pilot-operated electric proportional pressure reducing valve A206, a two-position three-way pilot-operated electric proportional pressure reducing valve B208 and a two-position three-way electromagnetic valve 212 respectively, and residual system pressure oil returns to an oil tank 209 and various lubricating points through a pressure reducing valve 213, a cooler 214 with a bypass and a one-way valve 215, wherein the pressure reducing valve 213 is used for adjusting the pressure of a lubricating oil path, and the one-way valve 215 plays a role in overpressure protection on the lubricating oil path; .
The working process of the hydraulic control system provided by the invention is as follows:
when the transmission is carried out according to the first gear transmission ratio, the two-position three-way pilot-operated electric proportional pressure reducing valve A206 controls the pressure and the stroke of the oil cylinder 211 of the wet clutch A, and the combination of the wet clutch A is realized.
When the transmission is carried out according to the second gear transmission ratio, the two-position three-way pilot-operated electric proportional pressure reducing valve B208 controls the pressure and the stroke of the oil cylinder 210 of the wet clutch B, and the combination of the wet clutch B is realized.
When the first gear is switched to the neutral gear or the second gear, the two-position three-way pilot-operated electro-proportional pressure reducing valve A206 controls the piston cavity of the wet clutch A oil cylinder 211 to be communicated with the oil tank 209, so that oil in the piston cavity of the wet clutch A oil cylinder 211 returns to the oil tank 209 under the left and right of the spring of the oil cylinder.
When the second gear is switched to the neutral gear or the first gear, the two-position three-way pilot-operated electro-proportional pressure reducing valve B208 controls the piston cavity of the wet clutch B cylinder 210 to be communicated with the oil tank 209, so that oil in the piston cavity of the wet clutch B cylinder 210 returns to the oil tank 209 under the left and right of the spring of the oil tank.
When the parking gear is not in the parking gear, the two-position three-way electromagnetic valve 212 controls pressure oil to enter the central wet parking brake oil cylinder 201, and overcomes the spring pressure of the oil cylinder to enable the parking brake to be in an uncompressed braking state; when the parking gear is in a parking gear, the two-position three-way electromagnetic valve 212 controls the piston cavity of the central wet parking brake cylinder 201 to be communicated with the oil tank 209, so that oil in the piston cavity of the central wet parking brake cylinder 201 returns to the oil tank 209 under the left and right of a spring of the piston cavity, and the parking brake is pressed by the spring of the central wet parking brake cylinder 201 and is in a braking state.
Claims (1)
1. An integrated two-gear speed change electric drive bridge with electronic parking comprises a transmission system and a hydraulic system, wherein the transmission system comprises a central wet parking brake, a low-gear driving gear, an input shaft, a high-gear driving gear, an elastic coupling, a driving motor, a high-gear driven gear, a wet clutch B, a wet clutch A, an intermediate shaft, a low-gear driven gear, an intermediate shaft gear, a left half shaft, an output shaft gear, a differential assembly and a right half shaft;
the driving motor transmits torque and rotating speed to the transmission input shaft, the low-gear driving gear and the high-gear driving gear through the elastic coupling, the low-gear driving gear transmits the torque and the rotating speed to the low-gear driven gear, and the high-gear driving gear transmits the torque and the rotating speed to the high-gear driven gear; the low-speed gear driven gear and the high-speed gear driven gear are both arranged on an intermediate shaft, and a central wet parking brake is also arranged on the intermediate shaft;
the wet clutch A and the wet clutch B are respectively meshed with the low-speed gear driven gear and the high-speed gear driven gear, and the torque and the rotating speed are output through the intermediate shaft gear to drive the differential mechanism assembly to drive the left half shaft and the right half shaft to rotate;
when the transmission is carried out according to the first gear transmission ratio, the wet clutch A is engaged, the low-speed gear driven gear transmits the torque and the rotating speed to the intermediate shaft gear through the intermediate shaft, and then the intermediate shaft gear outputs the shaft gear and the differential assembly to the left half shaft and the right half shaft through the torque and the rotating speed;
when the transmission is carried out according to the second gear transmission ratio, the wet clutch B is combined, the high-speed gear driven gear transmits the torque and the rotating speed to the intermediate shaft gear through the intermediate shaft, and then the intermediate shaft gear outputs the shaft gear and the differential assembly to the left half shaft and the right half shaft through the torque and the rotating speed;
when in neutral, neither wet clutch a nor wet clutch B is engaged;
when the brake is in a parking gear, the pressure of an oil cylinder piston cavity of the central wet parking brake is released by controlling the electromagnetic valve, and the friction plate is pressed tightly under the action of a spring of the brake to realize braking; and neither wet clutch a nor wet clutch B is engaged;
when the automobile is in a reverse gear, the reverse gear is realized by driving the motor to rotate reversely, and the reverse gear is consistent with the forward control mode;
the hydraulic system is a system integrating control and active lubrication and is used for providing a pressure oil source for the control and lubrication system by a gear oil pump driven by a constant-speed oil pump motor rotating in a single direction, so that the control pressure of the hydraulic system is kept constant;
the hydraulic system comprises a central wet parking brake oil cylinder, a magnetic filter, a filter with a pollution indicator and a bypass, a temperature sensor, a pilot overflow valve, a two-position three-way pilot electric proportional pressure reducing valve A, a gear oil pump, a two-position three-way pilot electric proportional pressure reducing valve B, an oil tank, a wet clutch B oil cylinder, a wet clutch A oil cylinder, a two-position three-way electromagnetic valve, a pressure reducing valve, a cooler with a bypass and a one-way valve; the gear oil pump pumps out system pressure oil in the oil tank, the system pressure oil is filtered by the magnetic filter and then enters the filter with a pollution indicator and a bypass and the temperature sensor, and a pilot-operated overflow valve is arranged at the tail end of the branch and used for adjusting the control pressure of the hydraulic system; the gear oil pump conveys system pressure oil into a wet clutch A oil cylinder, a wet clutch B oil cylinder and a central wet parking brake oil cylinder through a two-position three-way pilot-operated electric proportional pressure reducing valve A, a two-position three-way pilot-operated electric proportional pressure reducing valve B and a two-position three-way electromagnetic valve respectively, and residual system pressure oil returns to an oil tank and each lubricating point through a pressure reducing valve, a cooler with a bypass and a one-way valve, wherein the pressure reducing valve is used for adjusting the pressure of a lubricating oil path, and the one-way valve plays a role in overpressure protection on the lubricating oil path;
when transmission is carried out according to the first gear transmission ratio, the two-position three-way pilot-operated electric proportional pressure reducing valve A controls the pressure and the stroke of an oil cylinder of the wet clutch A, and the combination of the wet clutch A is realized;
when the transmission is carried out according to the second gear transmission ratio, the two-position three-way pilot-operated electric proportional pressure reducing valve B controls the pressure and the stroke of the oil cylinder of the wet clutch B, so that the combination of the wet clutch B is realized;
when the first gear is switched to a neutral gear or a second gear, the two-position three-way pilot-operated electric proportional pressure reducing valve A controls the communication between the piston cavity of the oil cylinder of the wet clutch A and the oil tank, so that oil in the piston cavity of the oil cylinder of the wet clutch A returns to the oil tank under the left and right of a spring of the oil cylinder of the wet clutch A;
when the second gear is switched to a neutral gear or a first gear, the two-position three-way pilot-operated electric proportional pressure reducing valve B controls the piston cavity of the oil cylinder of the wet clutch B to be communicated with the oil tank, so that oil in the piston cavity of the oil cylinder of the wet clutch B returns to the oil tank under the left and right of a spring of the oil cylinder of the wet clutch B;
when the parking gear is not in the parking gear, the two-position three-way electromagnetic valve controls pressure oil to enter the central wet parking brake oil cylinder, and the pressure of a spring of the oil cylinder is overcome to enable the parking brake to be in an uncompressed braking state;
when the parking gear is in a parking gear, the two-position three-way electromagnetic valve controls the communication between the piston cavity of the central wet parking brake oil cylinder and the oil tank, so that oil in the piston cavity of the central wet parking brake oil cylinder returns to the oil tank under the left and right of a spring of the central wet parking brake oil cylinder, and the parking brake is pressed by the spring of the central wet parking brake oil cylinder and is in a braking state.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810255809.7A CN108583273B (en) | 2018-03-27 | 2018-03-27 | Integrated two-gear variable-speed electric drive bridge with electronic parking function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810255809.7A CN108583273B (en) | 2018-03-27 | 2018-03-27 | Integrated two-gear variable-speed electric drive bridge with electronic parking function |
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| Publication Number | Publication Date |
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| CN108583273A CN108583273A (en) | 2018-09-28 |
| CN108583273B true CN108583273B (en) | 2021-08-17 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201810255809.7A Active CN108583273B (en) | 2018-03-27 | 2018-03-27 | Integrated two-gear variable-speed electric drive bridge with electronic parking function |
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| CN (1) | CN108583273B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110017359B (en) * | 2019-04-23 | 2021-03-09 | 合肥工业大学 | Multi-gear electric automobile transmission based on face gear |
| CN111391636A (en) * | 2020-04-28 | 2020-07-10 | 海茵茨曼动力控制（嘉兴）有限公司 | Electric motorcycle double-motor driving device and double-motor driving strategy thereof |
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| CN105235508A (en) * | 2015-11-09 | 2016-01-13 | 青岛科瑞特激光设备有限公司 | Two-gear four-wheel hydraulic stepless variable speed drive axle assembly for large harvester |
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| CN106763619A (en) * | 2017-01-22 | 2017-05-31 | 北京航空航天大学 | Two shift transmission used for electric vehicle |
| CN206826407U (en) * | 2017-06-27 | 2018-01-02 | 南京越博动力系统股份有限公司 | Two grades of transaxles of electric car |
| CN107627830A (en) * | 2017-09-21 | 2018-01-26 | 吉泰车辆技术（苏州）有限公司 | Integral shaft puts power assembly |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7240995B2 (en) * | 2003-05-06 | 2007-07-10 | Lexmark International, Inc. | Method of authenticating a consumable |
| CN202242966U (en) * | 2010-09-26 | 2012-05-30 | 比亚迪股份有限公司 | Driving system of electric vehicle |
| CN106812937A (en) * | 2015-12-01 | 2017-06-09 | 史树元 | A kind of planetary gear power dividing type stepless speed variator hydraulic control system |
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Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105235508A (en) * | 2015-11-09 | 2016-01-13 | 青岛科瑞特激光设备有限公司 | Two-gear four-wheel hydraulic stepless variable speed drive axle assembly for large harvester |
| CN205605780U (en) * | 2016-03-15 | 2016-09-28 | 绍兴前进齿轮箱有限公司 | Power dividing infinitely variable gear box |
| CN105762976A (en) * | 2016-04-18 | 2016-07-13 | 北京航空航天大学 | Blade electric vehicle integrated two-shift automatic electric drive assembly |
| CN106763619A (en) * | 2017-01-22 | 2017-05-31 | 北京航空航天大学 | Two shift transmission used for electric vehicle |
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| CN108583273A (en) | 2018-09-28 |
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