CN110056614B - Three-gear automatic transmission based on three-clutch electric automobile - Google Patents
Three-gear automatic transmission based on three-clutch electric automobile Download PDFInfo
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- CN110056614B CN110056614B CN201910329958.8A CN201910329958A CN110056614B CN 110056614 B CN110056614 B CN 110056614B CN 201910329958 A CN201910329958 A CN 201910329958A CN 110056614 B CN110056614 B CN 110056614B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/002—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having teeth movable out of mesh
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
- F16H3/22—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially
- F16H3/30—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial
- F16H3/32—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial and an additional shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
- F16H37/0813—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear Transmission (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates to a three-gear automatic transmission based on a three-clutch electric automobile, which is characterized in that the three-gear transmission consists of a main body transmission system, a three-clutch system, a brake system and a differential mechanism, and is connected through a worm gear, a worm and gear, a bevel gear and a dual gear, so that the three-gear automatic transmission has the advantages of compact structure and large transmission ratio adjusting range; the braking part adopts a structure that three clutches and gears are nested inside and outside, and the gears are switched by alternate braking; in addition, the parking brake part is realized by adopting a worm gear and a worm to reversely rotate and self-lock, so that the vehicle can be locked by a small torque. The invention has 3 forward gears, 1 parking gear and 1 neutral gear, has high transmission efficiency, compact structure and simple gear shifting mode, provides a new scheme reference for the structure of the power transmission system of the existing electric automobile, and has better use value and application prospect.
Description
Technical Field
The invention belongs to the field of electric automobile driving, and particularly relates to a three-gear automatic transmission based on a three-clutch electric automobile.
Background
Along with the national vigorous support and popularization of new energy automobiles, the new energy automobiles show the trend of increasing year by year, the electric automobiles are developed rapidly, the existing electric automobiles generally have the problems of insufficient power, low bearing capacity, high noise, poor gear selecting and shifting performance and the like, the driving and riding effects of the electric automobiles are influenced, and the existing electric automobiles have the problems of high power consumption and short service life of a transmission.
Patent CN105546073A discloses an electric drive system based on a two-stage planetary gear two-speed transmission, a first planetary gear sun gear connected with an output shaft of a drive motor; the first planet row planet gear is a duplicate gear and is fixedly connected with a first planet row planet carrier; a second sun gear duplicate gear meshed with the first planetary gear and the second planetary gear, respectively; the second planet row inner gear ring is fixedly connected with the driving system shell; the second planet row planet carrier is used as an output shaft.
Patent CN106195194A discloses a solution as follows: the planet row sun gear is simultaneously meshed with the first planet gear and the second planet gear, and the inner gear ring of the first planet row is fixed on the shell; the clutch is arranged between the planet carrier of the first planet row and the inner gear ring of the second planet row, and the rotation or fixation of the planet carrier is realized by controlling the closing of the clutch; the second planet row planet carrier is meshed with the differential case to output power.
The patent CN103953698A scheme takes a Simpson type compound planet row as a center, an input shaft is fixedly connected with a front sun gear and a rear sun gear, a front planet carrier is selectively connected with a shell through a second brake, and the front planet carrier and a rear ring gear are fixedly connected with a first brake through a third interconnecting member; the rear row of gear rings are fixedly connected with the output shaft through a second interconnecting component, and the adjustment of gears is realized by controlling the opening and closing of a brake.
Disclosure of Invention
Aiming at the problems of high energy consumption, large difference of high-low gear transmission ratio in an automatic transmission, difficult gear shifting and the like of the existing single transmission of the electric automobile, the invention designs a three-gear automatic transmission based on a three-clutch electric automobile with reasonable high, medium and low gear matching based on the transmission characteristics of a gear train and from the consideration of actual working conditions, and is beneficial to supplement the existing transmission of the electric automobile.
The invention adopts the following technical scheme for solving the technical problems:
a three-gear automatic transmission based on a three-clutch electric automobile is characterized in that the three-gear automatic transmission consists of a main body transmission system, a braking system, a three-clutch system and a differential mechanism; the main body transmission system is composed of a worm gear transmission set, a fixed shaft gear transmission set and a bevel gear transmission set; the worm and gear transmission set consists of a worm and a worm gear, the worm is meshed with the worm gear, and a first rotating shaft of the worm is fixedly connected with an output shaft of the motor; the fixed-axis gear transmission group consists of a duplex left gear, a first reduction gear wheel, a duplex right gear and a second reduction gear wheel; the duplex left gear is meshed with the first reduction gearwheel, and the duplex right gear is meshed with the second reduction gearwheel; the bevel gear transmission consists of a speed-increasing driving bevel gear and a speed-increasing driven bevel gear; the speed-increasing driving bevel gear is meshed with the speed-increasing driven bevel gear; the worm wheel is fixedly connected with the speed-increasing driving bevel gear, and the worm wheelThe rod, the duplex left gear and the duplex right gear are fixedly connected with the first rotating shaft; the brake system is composed of the worm, the worm wheel, the speed-increasing driving bevel gear, the speed-increasing driven bevel gear, a second rotating shaft, a third clutch, a speed-reducing driving bevel gear, a speed-reducing driven bevel gear and a planet carrier; the third clutch C3The outer ring is fixedly connected with the speed reduction driving bevel gear, and the inner ring of the third clutch is fixedly connected with the second rotating shaft; the speed reduction driving bevel gear is meshed with the speed reduction driven bevel gear, and the speed reduction driven bevel gear is fixedly connected with the planet carrier; the three-clutch system consists of a first clutch, a second clutch and a third clutch; the first clutch inner ring is fixedly connected with the second reduction gear wheel, the second clutch inner ring is fixedly connected with the first reduction gear wheel, and the third clutch inner ring is fixedly connected with the speed-increasing driven bevel gear through the second rotating shaft; the first clutch outer ring, the second clutch outer ring and the third clutch outer ring are fixedly connected with the speed reduction driving bevel gear.
Compared with the prior art, the invention has the beneficial effects that:
1. the invention adopts three clutches to realize gear shifting operation, and has the characteristics of compact structure, high gear shifting efficiency and small occupied space. The three clutches are matched with each other, the three-clutch-type transmission has three forward gears, a neutral gear and a parking gear, and can ensure that a gear is always in an engaged state in a gear shifting process by replacing a complicated gear shifting mechanism with the clutches, so that the gear shifting impact is small and the heat dissipation condition is good.
2. The first-gear speed reducing mechanism adopts worm gear transmission and bevel gear transmission, and has the advantages of large transmission ratio, compact structure, high bearing capacity, good stability and the like; the design requirements of road conditions in different areas can be met, and the adaptability is strong.
3. The worm of the invention adopts single-head Archimedes cylindrical worm for transmission, so that the parking mechanism is realized by self-locking of the worm and the gear, and the mechanism is greatly simplified.
Drawings
FIG. 1 is a schematic view of a gear transmission;
FIG. 2 is a first gear power transmission roadmap;
FIG. 3 is a two-gear power transmission route diagram;
FIG. 4 is a power transmission roadmap for gear three;
wherein: 1 worm, 2 worm gears, 3 speed-increasing driving bevel gears, 4 speed-increasing driven bevel gears, 5 duplex left gears, 6 first speed-reducing large gears, 7 duplex right gears, 8 second speed-reducing large gears, 9 speed-reducing driving bevel gears, 10 speed-reducing driven bevel gears, 11 differential left bevel gears, 12 differential upper bevel gears, 13 differential lower bevel gears, H planet carrier, C differential upper bevel gears, C differential lower bevel gears, C differential left bevel gears1First clutch, C2Second clutch, C3The third clutch, I first axis of rotation, II second axis of rotation, III third output shaft, IV fourth output shaft, M motor.
Detailed Description
As shown in figure 1, the invention relates to a three-gear automatic transmission based on a three-clutch electric automobile, which is characterized by mainly comprising a motor M, a first rotating shaft I, a worm gear, a bevel gear set, a three-clutch, a second rotating shaft II, a third output shaft III, a fourth output shaft IV, a differential and a shell.
The first rotating shaft I is fixedly connected with the duplex left gear 5 and the duplex right gear 6 through keys, the worm 1 is meshed with the worm wheel 2 to decelerate, the worm wheel 2 is fixedly connected with the speed-increasing large bevel gear 3, the speed-increasing driving bevel gear 3 is meshed with the speed-increasing driven bevel gear 4, and the speed-increasing driven bevel gear 4 and the speed-reducing driving bevel gear 9 are connected through a third clutch C3The reduction driving bevel gear 9 is meshed with the reduction driven bevel gear 10 to carry out secondary reduction, the reduction driven bevel gear 10 is fixedly connected with the planet carrier H to transmit power to the differential mechanism, and the differential mechanism is transmitted to wheels through a third output shaft III and a fourth output shaft IV; the left duplicate gear 5 and the right duplicate gear 7 are connected with the first rotating shaft I through keysThe duplex left gear 5 is meshed with a first reduction gearwheel 6, and the first reduction gearwheel 6 and a reduction driving bevel gear 9 pass through a second clutch C2The speed reduction driving bevel gear 9 is meshed with the speed reduction driven bevel gear 10 to carry out secondary speed reduction, the speed reduction driven bevel gear 10 is fixedly connected with the planet carrier H, and power is transmitted to the differential mechanism and distributed to the two wheels in the same way; meanwhile, the duplex right gear 7 is meshed with a second reduction gearwheel 8, and the second reduction gearwheel 8 and a reduction driving bevel gear 9 pass through a third clutch C3The differential mechanism is connected, the speed reduction driving bevel gear 9 is meshed with the speed reduction driven bevel gear 10 to carry out secondary speed reduction, the speed reduction driven bevel gear 10 is fixedly connected with a planet carrier H to transmit power to the differential mechanism, and the differential mechanism consists of a differential mechanism left bevel gear 11, a differential mechanism upper bevel gear 12 and a differential mechanism lower bevel gear 13; the three clutches are fixedly connected on the reduction driving bevel gear 9. The working principle of the invention is illustrated as follows:
according to the speed per hour requirement of the existing electric vehicle type and the requirement of special road conditions on vehicle speed reduction, the number of teeth of the designed gear is shown in table 1.
TABLE 1 Gear parameter table
The actuators for the various gears are shown in table 2.
2 Shift actuator worksheet
Note: in the table, "●" indicates binding and ". smallcircle" indicates separation;
with reference to fig. 1 and table 2, the transmission routes of the gears are described as follows:
1. neutral gear (N position)
In neutral, the first clutch C1And a second clutch C2Third clutch C3All are locatedIn the disengaged state, the electric motor M cannot transmit power to the reduction bevel gear 9, that is, to the differential, and the vehicle runs by inertia or is stationary.
2. Advance gear (D position)
(1) Advancing first gear (D1 gear)
As shown in FIG. 2, the motor rotates in the forward direction, the first clutch C1And a second clutch C2Kept disengaged, third clutch C3Combining, the worm 1 is meshed with the worm wheel 2 to reduce the speed, the worm wheel 2 is fixedly connected with the speed-increasing driving bevel gear 3, the speed-increasing driving bevel gear 3 is meshed with the speed-increasing driven bevel gear 4, and the speed-increasing driven bevel gear 4 and the speed-reducing driving bevel gear 9 are connected through a third clutch C3And the reduction driving bevel gear 9 is meshed with the reduction driven bevel gear 10 to reduce for the second time, the reduction driven bevel gear 10 is fixedly connected with the planet carrier H to transmit power to the differential mechanism, and the differential mechanism is transmitted to the wheels through the third output shaft III and the fourth output shaft IV.
(2) Two forward (D2 gear)
As shown in FIG. 3, the motor M rotates in the forward direction, and the first clutch C rotates in the forward direction1And a third clutch C3Kept disengaged, second clutch C2In combination, the duplex left gear 5 is meshed with the first reduction gearwheel 6, and the first reduction gearwheel 6 and the reduction drive bevel gear 9 pass through the second clutch C2And (3) connecting, wherein the speed reduction driving bevel gear 9 is meshed with the speed reduction driven bevel gear 10 to carry out secondary speed reduction, the speed reduction bevel gear 10 is fixedly connected with the planet carrier H, and power is transmitted to the differential mechanism and distributed to the two wheels.
(3) Advancing three-gear (D3 gear)
As shown in FIG. 4, the motor M rotates in the normal direction, and the second clutch C rotates in the normal direction2And a third clutch C3Kept disengaged, first clutch C1In combination, the duplex right gear 7 is meshed with a second reduction gearwheel 8, and the second reduction gearwheel 8 and a reduction drive bevel gear 9 pass through a clutch C3And the reduction bevel gear 9 is meshed with the reduction driven bevel gear 10 to reduce the speed for the second time, and the reduction driven bevel gear 10 is fixedly connected with the planet carrier H to transmit power to the speed reducer and distribute the power to the two wheels.
3. Gear shifting process
The first gear is shifted to the second gear, and the second clutch C is driven by the gear shifting control unit2Electrically engaged, third clutch C3First clutch C1Is in a disconnected state due to the power failure of the third clutch C3The power is separated from the first rotating shaft I through the duplex left gear 5, the first reduction gear 6 through the second clutch C2The speed is transmitted to the speed reduction driving bevel gear 9, the speed reduction driven bevel gear 10 and then the differential.
Two gears are shifted to three gears, and the first clutch C is shifted through the gear shifting control unit1Electrically engaged, second clutch C2Third clutch C3Disconnected in case of power failure due to the second clutch C2The power is separated from the first rotating shaft I through the duplex right gear 7 and the second reduction gear 8 through the first clutch C1The speed is transmitted to the speed reduction driving bevel gear 9, the speed reduction driven bevel gear 10 and then the differential.
The third gear is shifted to the first gear, and the third clutch C is shifted through the gear shifting control unit3Electrically engaged, first clutch C1Second clutch C2Disconnected in case of power failure due to clutch C1Separated, so that the power is transmitted from the first rotating shaft I through the worm gear and the worm and the clutch C3The speed is transmitted to the speed reduction driving bevel gear 9, the speed reduction driven bevel gear 10 and then the differential.
The third gear is shifted to the second gear, and the second clutch C is driven by the gear shifting control unit2Electrically engaged, first clutch C1Third clutch C3Disconnected in case of power failure due to the first clutch C1The power is separated from the first rotating shaft I through the duplex left gear 5, the first reduction gear 6 through the second clutch C2The speed is transmitted to the speed reduction driving bevel gear 9, the speed reduction driven bevel gear 10 and then the differential.
5. Parking (P position)
When the vehicle stops and needs to be parked, the third clutch C3And the worm wheel and the worm are reversely self-locked by electrifying combination.
Claims (1)
1. Three-gear automatic transmission based on three clutches for electric vehicleIs characterized in that the three-gear transmission consists of a main body transmission system, a braking system, a three-clutch system and a differential mechanism; the main body transmission system is composed of a worm gear transmission set, a fixed shaft gear transmission set and a bevel gear transmission set; the worm and gear transmission set is composed of a worm (1) and a worm gear (2), the worm (1) is meshed with the worm gear (2), and a first rotating shaft (I) of the worm (1) is fixedly connected with an output shaft of a motor (M); the dead axle gear transmission group consists of a duplex left gear (5), a first reduction gear wheel (6), a duplex right gear (7) and a second reduction gear wheel (8); the duplex left gear (5) is meshed with the first reduction gearwheel (6), and the duplex right gear (7) is meshed with the second reduction gearwheel (8); the bevel gear transmission consists of a speed-increasing driving bevel gear (3) and a speed-increasing driven bevel gear (4); the speed-increasing driving bevel gear (3) is meshed with the speed-increasing driven bevel gear (4); the worm wheel (2) is fixedly connected with the speed-increasing driving bevel gear (3), and the worm (1), the duplex left gear (5) and the duplex right gear (7) are fixedly connected with the first rotating shaft (I); the braking system consists of the worm (1), the worm wheel (2), the speed-increasing driving bevel gear (3), the speed-increasing driven bevel gear (4), a second rotating shaft (II) and a third clutch C3The speed reduction driving bevel gear (9), the speed reduction driven bevel gear (10) and the planet carrier (H); the third clutch C3The outer ring is fixedly connected with the speed reduction drive bevel gear (9), and the third clutch C3The inner ring is fixedly connected with the second rotating shaft (II); the speed reduction driving bevel gear (9) is meshed with the speed reduction driven bevel gear (10), and the speed reduction driven bevel gear (10) is fixedly connected with the planet carrier (H); the three-clutch system consists of a first clutch C1A second clutch C2The third clutch C3Forming; the first clutch C1The inner ring is fixedly connected with the second reduction gear wheel (8), and the second clutch C2The inner ring is fixedly connected with a first reduction gear wheel (6), and the third clutch C3The inner ring is fixedly connected with the speed-increasing driven bevel gear (4) through the second rotating shaft (II); the first clutch C1Outer race, the second clutch C2Outer ring, the third clutch C3Outer ring and said damperThe fast driving bevel gear (9) is fixedly connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910329958.8A CN110056614B (en) | 2019-04-23 | 2019-04-23 | Three-gear automatic transmission based on three-clutch electric automobile |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910329958.8A CN110056614B (en) | 2019-04-23 | 2019-04-23 | Three-gear automatic transmission based on three-clutch electric automobile |
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| CN110056614A CN110056614A (en) | 2019-07-26 |
| CN110056614B true CN110056614B (en) | 2020-08-21 |
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| CN201910329958.8A Active CN110056614B (en) | 2019-04-23 | 2019-04-23 | Three-gear automatic transmission based on three-clutch electric automobile |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111810552B (en) * | 2020-07-20 | 2021-10-26 | 合肥工业大学 | Stepped n-gear wet clutch structure |
| CN112973006A (en) * | 2021-04-16 | 2021-06-18 | 康建民 | Speed-adjustable running machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030000325A1 (en) * | 2001-06-28 | 2003-01-02 | Hoehn Richard T. | Multi-speed worm gear reduction assembly |
| CN202392056U (en) * | 2011-11-24 | 2012-08-22 | 郑方焱 | Continuously-variable transmission for non-conical gears |
| CN103953698B (en) * | 2014-04-30 | 2016-08-03 | 北京航空航天大学 | A kind of electrically driven (operated) planetary transmission |
| CN105546073A (en) * | 2016-01-22 | 2016-05-04 | 吉林大学 | Electric drive system based on two-stage planetary line two-shift transmission |
| CN208364707U (en) * | 2018-06-20 | 2019-01-11 | 浙江吉利控股集团有限公司 | Three clutch hybrid gearboxes |
| CN109268454A (en) * | 2018-11-19 | 2019-01-25 | 淮南联合大学 | A kind of worm-gear type two keeps off speed change gear and its method for changing speed |
| CN109340325A (en) * | 2018-11-19 | 2019-02-15 | 淮南联合大学 | A kind of new type worm wheel formula speed changer and its method for changing speed |
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