CN201992008U - Transmission and vehicle including same - Google Patents
Transmission and vehicle including same Download PDFInfo
- Publication number
- CN201992008U CN201992008U CN 201120087561 CN201120087561U CN201992008U CN 201992008 U CN201992008 U CN 201992008U CN 201120087561 CN201120087561 CN 201120087561 CN 201120087561 U CN201120087561 U CN 201120087561U CN 201992008 U CN201992008 U CN 201992008U
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- China
- Prior art keywords
- gear
- clutch
- input shaft
- speed changer
- output shaft
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- Expired - Lifetime
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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
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A transmission comprises a double clutch, a first input shaft, a second input shaft and an output shaft, wherein the double clutch comprises a first clutch and a second clutch, the first input shaft is connected with the first clutch, and the second input shaft penetrates through a cavity portion of the first input shaft to be connected with the second clutch. The transmission further comprises a planetary gear mechanism, a one-way clutch and a gear reduction mechanism, a sun wheel is fixed on a transmission casing, a gear ring is fixedly connected with the first input shaft, the one-way clutch is installed between a planet carrier and the second input shaft, and motive power is transmitted between the second input shaft and the output shaft through the gear reduction mechanism. The utility model further provides a vehicle. Due to the planetary gear mechanism and the one-way clutch, the second input shaft can not only directly transmit the motive power input by the second clutch, but also transmit the motive power input by the first clutch, thereby saving one output shaft, being compact in structure of the clutch and small in covered space.
Description
Technical field
The utility model relates to a kind of speed changer and comprises the vehicle of this speed changer.
Background technique
At present, along with the fast development of trailer reversing automation, automotive transmission is just presenting rapid growth momentum.Present automatic gearbox mainly contains torque converter (AT), stepless speed variator (CVT) and the present high electric control mechanical speed changer (AMT) of transmission efficiency.
The AMT that is better than AT and CVT at aspects such as transmission efficiency and cost of production because it has the advantage of the existing manual transmission production investment of the desired high fuel economy of automobile industry development, low emission and protection, has been subjected to the attention of motor-dom.
But in the using process of AMT, find its shortcoming gradually: vehicle is in shift process, and after clutch separation, the power of motor can not be delivered to wheel, causes power interruption, and the driver has the pause and transition in rhythm or melody sense, has influenced the power character of vehicle and the travelling comfort of taking.
For head it off, need control accurately shift process.Particularly, need the power assembly of power plant and speed changer formation be mated accurately at aspects such as speed discrepancy, moments of torsion and control in order to reduce the shock extent that shift process produces.
The DCT(dual-clutch transmission) appearance has solved this problem.But DCT has two input shafts and two output shafts, and it is bigger to occupy the space.
Summary of the invention
The utility model is for solving the existing dual-clutch transmission bigger technical problem that takes up room, and a kind of little speed changer and comprise the vehicle of this speed changer of taking up room is provided.
The utility model provides a kind of speed changer on the one hand, comprise: double clutch, first input shaft of hollow, second input shaft and output shaft, described double clutch comprises first clutch and second clutch, described first input shaft is connected with first clutch, the hollow space that described second input shaft passes described first input shaft is connected with described second clutch, wherein, described speed changer also comprises planetary gears, overrunning clutch and reduction gears mechanism, described planetary gears comprises sun gear, planet carrier and gear ring, described sun gear is fixed on the housing of speed changer, described gear ring is fixedlyed connected with described first input shaft, described overrunning clutch be installed between the described planet carrier and second input shaft so that from planetary gears to the second input shaft unidirectional delivery power, between described second input shaft and the output shaft by the reduction gears mechanism transferring power.
Further, described overrunning clutch comprises inner ring and outer ring, when the rotating speed of outer ring is higher than the rotating speed of inner ring, overrunning clutch is in bonding state, when the rotating speed of inner ring is higher than the rotating speed of outer ring, overrunning clutch is in and surmounts state, and the inner ring of described overrunning clutch is fixed on described second input shaft, and described planet carrier is sleeved on the outer ring of described overrunning clutch.
Described reduction gears mechanism comprises first gear train, second gear train and synchronizer, described first gear train comprises intermeshing first gear and second gear, described second gear train comprises intermeshing the 3rd gear and the 4th gear, described first gear and the 3rd gear all are fixed on described second input shaft, described second gear and the equal sky of the 4th gear are enclosed within on the described output shaft, on the output shaft between described second gear and the 4th gear synchronizer are installed.
Described reduction gears mechanism also comprises the reverse gear group, described reverse gear group comprises the 5th gear, idle pulley and the 6th gear, described the 5th gear is fixed on described second input shaft, described the 6th gear is fixed on the described output shaft, passes through the idle pulley transferring power between described the 5th gear and the 6th gear.
Described speed changer also comprises reverse gear shaft, and described idle pulley is installed on the described reverse gear shaft.
Also be fixed with output gear on the described output shaft.
When described synchronizer and described the 4th gear were synchronous: described first clutch combined, and described second clutch separates, and described planetary gears cooperates with described second gear train realizes first gear; Described first clutch separates, described second clutch combination, and described second gear train constitutes second gear.
When described synchronizer and described second gear were synchronous: described first clutch combined, and described second clutch separates, and described planetary gears cooperates with described first gear train realizes the 3rd gear; Described first clutch separates, described second clutch combination, and described first gear train constitutes the 4th gear.
When described synchronizer disconnects: described first clutch combination, described second clutch separates, and the realization low speed gear that reverses gear is closed in described planetary gears and described reverse gear assembly; Described first clutch separates, described second clutch combination, and described reverse gear group constitutes the gear that reverses gear at a high speed.
The utility model also provides a kind of vehicle on the other hand, comprises power source and differential mechanism, and wherein, described vehicle also comprises above-mentioned speed changer, and described power source is connected with the double clutch of described speed changer, and the output shaft of described speed changer is connected with described differential mechanism.
Speed changer of the present utility model and comprise the vehicle of this speed changer, be provided with planetary gears and overrunning clutch, thereby the power that makes the input shaft of winning can unidirectional delivery to second input shaft and then output, promptly second input shaft can also transmit the power of first clutch input except the power of direct transmission second clutch input, therefore can save an output shaft, and then make that this speed changer structure is compact, it is less to take up room.
Description of drawings
Fig. 1 is the structural representation sketch of the speed changer that provides of a kind of mode of execution of the utility model;
Fig. 2 is speed changer that a kind of mode of execution of the utility model the provides state simplified schematic diagram when being in first gear, and wherein, heavy line is represented power transmission line;
Fig. 3 is speed changer that a kind of mode of execution of the utility model the provides state simplified schematic diagram when being in second gear, and wherein, heavy line is represented power transmission line;
Fig. 4 is speed changer that a kind of mode of execution of the utility model the provides state simplified schematic diagram when being in the 3rd gear, and wherein, heavy line is represented power transmission line;
Fig. 5 is speed changer that a kind of mode of execution of the utility model the provides state simplified schematic diagram when being in the 4th gear, and wherein, heavy line is represented power transmission line;
Fig. 6 is speed changer that a kind of mode of execution of the utility model the provides state simplified schematic diagram when being in low speed and reversing gear gear, and wherein, heavy line is represented power transmission line;
Fig. 7 is that speed changer that a kind of mode of execution of the utility model provides is in the state simplified schematic diagram when reversing gear gear at a high speed, and wherein, heavy line is represented power transmission line;
Fig. 8 is the structural representation sketch of the vehicle that provides of a kind of mode of execution of the utility model.
Embodiment
Clearer for technical problem, technological scheme and beneficial effect that the utility model is solved, below in conjunction with drawings and Examples, the utility model is further elaborated.Should be appreciated that specific embodiment described herein only in order to explanation the utility model, and be not used in qualification the utility model.
According to a kind of mode of execution of the present utility model, as shown in Figure 1, a kind of speed changer, comprise: double clutch 1, first input shaft 4 of hollow, second input shaft 8 and output shaft 20, double clutch 1 comprises first clutch 3 and second clutch 2, first input shaft 4 is connected with first clutch 3, the hollow space that second input shaft 8 passes first input shaft 4 is connected with second clutch 2, wherein, this speed changer also comprises planetary gears 23, overrunning clutch 7 and reduction gears mechanism 27, planetary gears 23 comprises sun gear 22, planet carrier 6 and gear ring 5, sun gear 22 is fixed on the housing (not shown) of speed changer, gear ring 5 is fixedlyed connected with first input shaft 4, overrunning clutch 7 be installed between the planet carrier 6 and second input shaft 8 so that from planetary gears 23 to second input shaft, 8 unidirectional delivery power, between second input shaft 8 and the output shaft 20 by reduction gears mechanism 27 transferring power.
Usually, for component such as input shaft and output shaft are installed, speed changer comprises housing, and double clutch 1, first input shaft 14, second input shaft 8, output shaft 20, planetary gears 23, overrunning clutch 7 and reduction gears mechanism 27 are installed in the housing.
Known ground, planetary gears 23 comprises sun gear 22, planet carrier 6 and gear ring 5, constitute connection by a plurality of as 3 planet wheels between sun gear 22 and the gear ring 5, planet carrier 6 is connected with all planet wheel, in sun gear 22, planet carrier 6 and gear ring 5 threes, fix one, remain and get final product one among both and import power, outputting powers.
Those skilled in the art can rationally be provided with the size of planetary gears 23 as required, and select fixedly sun gear 22, planet carrier 6 and gear ring 5 threes', thereby form suitable reduction speed ratio.
Any one fixing all can realize among sun gear 22, planet carrier 6 and gear ring 5 threes by various suitable devices, as utilize break realization etc.
According to a kind of mode of execution of the present utility model, sun gear 22 directly is fixed on the housing of speed changer, and gear ring 5 is fixedlyed connected as power intake with first input shaft 4, and planet carrier 6 is connected as clutch end with overrunning clutch 7.
Further, overrunning clutch 7 comprises inner ring and outer ring, when the rotating speed of outer ring is higher than the rotating speed of inner ring, overrunning clutch 7 is in bonding state, when the rotating speed of inner ring is higher than the rotating speed of outer ring, overrunning clutch 7 is in and surmounts state, and the inner ring of overrunning clutch 7 is fixed on second input shaft 8, and planet carrier 6 is sleeved on the outer ring of overrunning clutch 7.
The effect of overrunning clutch is to make certain element rotate locking on another direction by certain direction.According to different roller-type overrunning clutch and the free wheeling sprag clutchs of being divided into of the transmission of power device of installing between inner ring and the outer ring (as roller or voussoir).Those skilled in the art can select the overrunning clutch of adequate types as required.
According to a kind of mode of execution of the present utility model, when the rotating speed of outer ring was higher than the rotating speed of inner ring, overrunning clutch 7 was in bonding state, and power can be delivered to second input shaft 8 from planetary gears 23; When the rotating speed of inner ring was higher than the rotating speed of outer ring, overrunning clutch 7 was in and surmounts state, and at this moment, the power of second input shaft 8 can not be delivered to planetary gears 23.
Further, reduction gears mechanism 27 comprises first gear train 9, second gear train 11 and synchronizer 18, first gear train 9 comprises intermeshing first gear 21 and second gear 19, second gear train 11 comprises intermeshing the 3rd gear 10 and the 4th gear 17, first gear 21 and the 3rd gear 10 all are fixed on second input shaft 8, second gear 19 and the 4th gear 17 equal skies are enclosed within on the output shaft 20, on the output shaft 20 between second gear 19 and the 4th gear 17 synchronizer 18 are installed.
Synchronizer 18 can with second gear 19 synchronously so that first gear train, 9 transferring power, synchronizer 18 can also with the 4th gear 17 synchronously so that second gear train, 11 transferring power.
In order to realize reversing gear, reduction gears mechanism 27 also comprises reverse gear group 26, reverse gear group 26 comprises the 5th gear 12, idle pulley 13 and the 6th gear 14, the 5th gear 12 is fixed on second input shaft 8, the 6th gear 14 is fixed on the output shaft 20, passes through idle pulley 13 transferring power between the 5th gear 12 and the 6th gear 14.
For idle pulley 13 is installed, this speed changer also comprises reverse gear shaft 15, and idle pulley 13 is installed on the reverse gear shaft 15.When needs are moveed backward, can make idle pulley 13 mesh with the 5th gear 12 and the 6th gear 14 simultaneously by handling gear level, thereby finish the transmission of power of reversing gear.
For outputting power, on output shaft 20, also be fixed with output gear 16 so that will be input to the power of speed changer and output to wheel (by realizations such as differential mechanisms).
According to a kind of mode of execution of the present utility model, when synchronizer 18 with the 4th gear 17 synchronously the time: first clutch 3 combines, and second clutch 2 separates, and planetary gears 23 cooperates realization first gear with second gear train 11; First clutch 3 separates, second clutch 2 combinations, and second gear train 11 constitutes second gear.
When synchronizer 18 with second gear 19 synchronously the time: first clutch 3 combines, and second clutch 2 separates, and planetary gears 23 cooperates realization the 3rd gear with first gear train 9; First clutch 3 separates, second clutch 2 combinations, and first gear train 9 constitutes the 4th gear.
When synchronizer 18 disconnected (neither synchronous with second gear 19, also not synchronous with the 4th gear 17): first clutch 3 combined, and second clutch 2 separates, and planetary gears 23 cooperates the realization low speed gear that reverses gear with reverse gear group 26; First clutch 3 separates, second clutch 2 combinations, and reverse gear group 26 constitutes the gear that reverses gear at a high speed.
Describe the gear handoff procedure of speed changer of the present utility model in detail below in conjunction with accompanying drawing:
According to a kind of mode of execution of the present utility model, as shown in Figure 2, synchronizer 18 and the 4th gear 17 are synchronously the time, 3 combinations of control first clutch, second clutch 2 separates, power successively from first clutch 3, first input shaft 4, gear ring 5, planet carrier 6, overrunning clutch 7(at this moment, the rotating speed of second input shaft 8 will be lower than the rotating speed of planet carrier 6 outputs, be the rotating speed that the rotating speed of the outer ring of overrunning clutch 7 is higher than inner ring, overrunning clutch 7 is in bonding state), second input shaft 8 and second gear train 11 be delivered to the output gear 16 on the output shaft 20.In this process, planetary gears 23 and second gear train, the 11 common velocity ratios that form first gear are promptly realized the switching of first gear.
According to a kind of mode of execution of the present utility model, as shown in Figure 3, synchronizer 18 continues with the 4th gear 17 synchronous, at this moment, control first clutch 3 separates, second clutch 2 combinations, power will be successively be delivered to output gear 16 on the output shaft 20 from second clutch 2, second input shaft 8 and second gear train 11.In this process, because the rotating speed that the rotating speed of second input shaft 8 is higher than planet carrier 6 (at this moment, the rotating speed of planet carrier 6 can be zero), be the rotating speed that the rotating speed of the outer ring of overrunning clutch 7 is lower than inner ring, overrunning clutch 7 is in and surmounts state, at this moment, the power of second input shaft 8 can not be delivered to first input shaft 4, planetary gears 23 is inoperative, so second gear train 11 forms second gear separately.
Hence one can see that, and the switching of first gear and second gear only needs the first clutch 3 in the control double clutch 1 to replace combination and separate and can realize with second clutch 2, thereby effectively reduces the dynamic impact in the shift process, improves the riding comfort of vehicle.
According to a kind of mode of execution of the present utility model, as shown in Figure 4, the synchronizer 18 and second gear 19 are (at this moment synchronously, make that by gear level synchronizer 18 is from switching to and second gear, 19 synchronization position with the 4th gear 19 synchronization position), 3 combinations of control first clutch, second clutch 2 separates, power is successively from first clutch 3, first input shaft 4, gear ring 5, planet carrier 6, overrunning clutch 7(at this moment, the rotating speed of second input shaft 8 will be lower than the rotating speed of planet carrier 6 outputs, be the rotating speed that the rotating speed of the outer ring of overrunning clutch 7 is higher than inner ring, overrunning clutch 7 is in bonding state), second input shaft 8 and first gear train 9 are delivered to the output gear 16 on the output shaft 20.In this process, planetary gears 23 and first gear train, the 9 common velocity ratios that form the 3rd gear are promptly realized the switching of the 3rd gear.
According to a kind of mode of execution of the present utility model, as shown in Figure 5, synchronizer 18 continues with second gear 19 synchronous, at this moment, control first clutch 3 separates, second clutch 2 combinations, power will be successively be delivered to output gear 16 on the output shaft 20 from second clutch 2, second input shaft 8 and first gear train 9.In this process, because the rotating speed that the rotating speed of second input shaft 8 is higher than planet carrier 6 (at this moment, the rotating speed of planet carrier 6 can be zero), be the rotating speed that the rotating speed of the outer ring of overrunning clutch 7 is lower than inner ring, overrunning clutch 7 is in and surmounts state, at this moment, the power of second input shaft 8 can not be delivered to first input shaft 4, planetary gears 23 is inoperative, so first gear train 9 forms the 4th gear separately.
Hence one can see that, and the switching of the 3rd gear and the 4th gear only needs the first clutch 3 in the control double clutch 1 to replace combination and separate and can realize with second clutch 2, thereby effectively reduces the dynamic impact in the shift process, improves the riding comfort of vehicle.
According to a kind of mode of execution of the present utility model, as shown in Figure 6, synchronizer 18 is in initial position (being that synchronizer disconnects), and promptly this moment, synchronizer 18 was neither synchronous with second gear 19, also not synchronous with the 4th gear 17.3 combinations of control first clutch, second clutch 2 separates, power successively from first clutch 3, first input shaft 4, gear ring 5, planet carrier 6, overrunning clutch 7(at this moment, the rotating speed of second input shaft 8 will be lower than the rotating speed of planet carrier 6 outputs, it is the rotating speed that the rotating speed of the outer ring of overrunning clutch 7 is higher than inner ring, overrunning clutch 7 is in bonding state), second input shaft 8 and reverse gear group 26(this moment, switch to and reverse gear by handling gear level, idle pulley 13 simultaneously and the 5th gear 12 and 14 engagements of the 6th gear) be delivered to the output gear 16 on the output shaft 20.In this process, planetary gears 23 and reverse gear group 26 be common to form the reverse gear velocity ratio of gear of low speed, promptly realizes the reverse gear switching of gear of low speed.
According to a kind of mode of execution of the present utility model, as shown in Figure 7, synchronizer 18 keeps initial position, control first clutch 3 separates, second clutch 2 combinations, power will be successively be delivered to output gear 16 on the output shaft 20 from second clutch 2, second input shaft 8 and second gear train 11.In this process, because the rotating speed that the rotating speed of second input shaft 8 is higher than planet carrier 6 (at this moment, the rotating speed of planet carrier 6 can be zero), be the rotating speed that the rotating speed of the outer ring of overrunning clutch 7 is lower than inner ring, overrunning clutch 7 is in and surmounts state, at this moment, the power of second input shaft 8 can not be delivered to first input shaft 4, planetary gears 23 is inoperative, so reverse gear group 26 forms the gear that reverses gear at a high speed separately.
Hence one can see that, the reverse gear switching of the gear and the gear that reverses gear at a high speed of low speed, only need the first clutch 3 in the control double clutch 1 to replace combination and separate and to realize, thereby effectively reduce the dynamic impact in the shift process, improve the riding comfort of vehicle with second clutch 2.
When first clutch 3 all separates with second clutch 2, power interruption, can realize neutral this moment.
According to a kind of mode of execution of the present utility model, as shown in Figure 8, the utility model also provides a kind of vehicle on the other hand, comprise power source 24 and differential mechanism 25, wherein, this vehicle also comprises above-mentioned speed changer, and power source 24 is connected with the double clutch 1 of speed changer, and the output shaft 20 of speed changer is connected with differential mechanism 25.
Speed changer of the present utility model and comprise the vehicle of this speed changer, be provided with planetary gears and overrunning clutch, thereby the power that makes the input shaft of winning can unidirectional delivery to second input shaft and then output, promptly second input shaft can also transmit the power of first clutch input except the power of direct transmission second clutch input, therefore can save an output shaft, and then make that this speed changer structure is compact, it is less to take up room.
In addition, be provided with reduction gears mechanism between second input shaft and output shaft, reduction gears mechanism cooperates with planetary gears can realize a plurality of gears, thereby helps improving the power source especially power line and the Economy of motor.
Simultaneously, can realize switching by the control double clutch between the odd even gear (as first gear and second gear, the 3rd gear and the 4th gear) that same gear train forms, thereby effectively reduce the dynamic impact in the shift process, realize the free of discontinuities gearshift, improve the riding comfort of vehicle.
And synchronizer and a gear train are when synchronous, by control in the double clutch first clutch and second clutch alternately in conjunction with realizing two gears with separating, so the control by double clutch can make a synchronizer can realize four gears, help simplifying the structure of speed changer, make speed changer compact more, also simplified the operation of gearshift simultaneously.
The above only is preferred embodiment of the present utility model; not in order to restriction the utility model; all any modifications of within spirit of the present utility model and principle, being done, be equal to and replace and improvement etc., all should be included within the protection domain of the present utility model.
Claims (10)
1. speed changer, comprise: double clutch, first input shaft of hollow, second input shaft and output shaft, described double clutch comprises first clutch and second clutch, described first input shaft is connected with first clutch, the hollow space that described second input shaft passes described first input shaft is connected with described second clutch, it is characterized in that, described speed changer also comprises planetary gears, overrunning clutch and reduction gears mechanism, described planetary gears comprises sun gear, planet carrier and gear ring, described sun gear is fixed on the housing of speed changer, described gear ring is fixedlyed connected with described first input shaft, described overrunning clutch be installed between the described planet carrier and second input shaft so that from planetary gears to the second input shaft unidirectional delivery power, between described second input shaft and the output shaft by the reduction gears mechanism transferring power.
2. speed changer as claimed in claim 1, it is characterized in that, described overrunning clutch comprises inner ring and outer ring, when the rotating speed of outer ring is higher than the rotating speed of inner ring, overrunning clutch is in bonding state, and when the rotating speed of inner ring was higher than the rotating speed of outer ring, overrunning clutch was in and surmounts state, the inner ring of described overrunning clutch is fixed on described second input shaft, and described planet carrier is sleeved on the outer ring of described overrunning clutch.
3. speed changer as claimed in claim 1, it is characterized in that, described reduction gears mechanism comprises first gear train, second gear train and synchronizer, described first gear train comprises intermeshing first gear and second gear, described second gear train comprises intermeshing the 3rd gear and the 4th gear, described first gear and the 3rd gear all are fixed on described second input shaft, described second gear and the equal sky of the 4th gear are enclosed within on the described output shaft, on the output shaft between described second gear and the 4th gear synchronizer are installed.
4. speed changer as claimed in claim 3, it is characterized in that, described reduction gears mechanism also comprises the reverse gear group, described reverse gear group comprises the 5th gear, idle pulley and the 6th gear, described the 5th gear is fixed on described second input shaft, described the 6th gear is fixed on the described output shaft, passes through the idle pulley transferring power between described the 5th gear and the 6th gear.
5. speed changer as claimed in claim 4 is characterized in that described speed changer also comprises reverse gear shaft, and described idle pulley is installed on the described reverse gear shaft.
6. speed changer as claimed in claim 4 is characterized in that, also is fixed with output gear on the described output shaft.
7. speed changer as claimed in claim 3 is characterized in that, when described synchronizer and described the 4th gear were synchronous: described first clutch combined, and described second clutch separates, and described planetary gears cooperates with described second gear train realizes first gear; Described first clutch separates, described second clutch combination, and described second gear train constitutes second gear.
8. speed changer as claimed in claim 7 is characterized in that, when described synchronizer and described second gear were synchronous: described first clutch combined, and described second clutch separates, and described planetary gears cooperates with described first gear train realizes the 3rd gear; Described first clutch separates, described second clutch combination, and described first gear train constitutes the 4th gear.
9. speed changer as claimed in claim 4 is characterized in that, when described synchronizer disconnects: described first clutch combination, described second clutch separates, and the realization low speed gear that reverses gear is closed in described planetary gears and described reverse gear assembly; Described first clutch separates, described second clutch combination, and described reverse gear group constitutes the gear that reverses gear at a high speed.
10. vehicle, comprise power source and differential mechanism, it is characterized in that described vehicle also comprises any described speed changer among the claim 1-9, described power source is connected with the double clutch of described speed changer, and the output shaft of described speed changer is connected with described differential mechanism.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201120087561 CN201992008U (en) | 2011-03-30 | 2011-03-30 | Transmission and vehicle including same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201120087561 CN201992008U (en) | 2011-03-30 | 2011-03-30 | Transmission and vehicle including same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201992008U true CN201992008U (en) | 2011-09-28 |
Family
ID=44668497
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201120087561 Expired - Lifetime CN201992008U (en) | 2011-03-30 | 2011-03-30 | Transmission and vehicle including same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201992008U (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102720809A (en) * | 2011-03-30 | 2012-10-10 | 比亚迪股份有限公司 | A speed changer and a vehicle including the speed changer |
| CN102878259A (en) * | 2012-09-28 | 2013-01-16 | 长城汽车股份有限公司 | Multispeed automatic transmission and power assembly |
| CN106321808A (en) * | 2015-07-01 | 2017-01-11 | 现代自动车株式会社 | Transmission for vehicle |
| CN106931096A (en) * | 2015-12-31 | 2017-07-07 | 重庆硬核派传动科技有限公司 | A kind of dual input shaft three-speed gear |
| CN110206856A (en) * | 2019-06-20 | 2019-09-06 | 刘正民 | Manual push-pull driving mechanism |
| CN112984106A (en) * | 2020-04-02 | 2021-06-18 | 天津叠挡传动技术有限公司 | Clutch device with overlapped gears, speed changing device, power generation device and electric automobile |
| CN114060479A (en) * | 2021-11-16 | 2022-02-18 | 贵州凯星液力传动机械有限公司 | Transmission mechanism |
-
2011
- 2011-03-30 CN CN 201120087561 patent/CN201992008U/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102720809A (en) * | 2011-03-30 | 2012-10-10 | 比亚迪股份有限公司 | A speed changer and a vehicle including the speed changer |
| CN102720809B (en) * | 2011-03-30 | 2016-03-02 | 比亚迪股份有限公司 | A kind of speed changer and comprise the vehicle of this speed changer |
| CN102878259A (en) * | 2012-09-28 | 2013-01-16 | 长城汽车股份有限公司 | Multispeed automatic transmission and power assembly |
| CN102878259B (en) * | 2012-09-28 | 2015-11-11 | 长城汽车股份有限公司 | A kind of many gears automatic transmission and power assembly |
| CN106321808A (en) * | 2015-07-01 | 2017-01-11 | 现代自动车株式会社 | Transmission for vehicle |
| CN106321808B (en) * | 2015-07-01 | 2019-09-24 | 现代自动车株式会社 | Transmission for a vehicle |
| CN106931096A (en) * | 2015-12-31 | 2017-07-07 | 重庆硬核派传动科技有限公司 | A kind of dual input shaft three-speed gear |
| CN110206856A (en) * | 2019-06-20 | 2019-09-06 | 刘正民 | Manual push-pull driving mechanism |
| CN112984106A (en) * | 2020-04-02 | 2021-06-18 | 天津叠挡传动技术有限公司 | Clutch device with overlapped gears, speed changing device, power generation device and electric automobile |
| CN114060479A (en) * | 2021-11-16 | 2022-02-18 | 贵州凯星液力传动机械有限公司 | Transmission mechanism |
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