CN201841948U - Dual clutch transmission driver - Google Patents
Dual clutch transmission driver Download PDFInfo
- Publication number
- CN201841948U CN201841948U CN2010205517257U CN201020551725U CN201841948U CN 201841948 U CN201841948 U CN 201841948U CN 2010205517257 U CN2010205517257 U CN 2010205517257U CN 201020551725 U CN201020551725 U CN 201020551725U CN 201841948 U CN201841948 U CN 201841948U
- Authority
- CN
- China
- Prior art keywords
- retaining
- gear
- gears
- output shaft
- clutch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- 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
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
-
- 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
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The utility model relates to a dual clutch transmission driver comprising an inner input shaft and an outer input shaft which are coaxially arranged, and also comprising a first output shaft, a second output shaft, gears on all the shafts, two clutches and four synchronizers, wherein a third-gear driving gear is also taken as a fifth-gear driving gear; a fourth-gear driving gear is also taken as a sixth-gear driving gear; a second-gear driving gear is also taken as a reverse-gear driving gear; the dual clutch transmission driver is also provided with a reverse-gear shaft; a reverse-gear shaft hollow sleeve is provided with a reverse-gear idle gear; a first synchronizer can optionally transmit the torsion of first and third gears to the first output shaft; a second synchronizer can optionally transmit the torsion of a fourth gear and a reverse gear to the first output shaft; a third synchronizer can optionally transmit the torsion of sixth and second gears to the second output shaft; and a fourth synchronizer can optionally transmit the torsion of a fifth gear to the second output shaft. Under equal torsion, the axial length of the transmission can be shortened; and the speed distribution of the transmission is optimized while a plurality of pairs of gears are shared.
Description
Technical field
The utility model belongs to the Automotive transmission technical field, is specifically related to the dual-clutch transmission driving device.
Background technology
Representative type dual-clutch transmission driving device refers to by two power-transfer clutchs and is connected with two input shafts respectively, transmits engine power.Double clutch transmissions is by two coaxial nested or power-transfer clutchs of being arranged in parallel, two input shafts of coaxial, inside and outside nested arrangement, two output shafts that are arranged in parallel are arranged in a plurality of synchromesh gears on the output shaft, a plurality of selector fork and 1 diff and form.Change-speed box is strange, even number retaining input gear is arranged on two input shafts, and switching and the action of different synchro by two power-transfer clutchs realize torque conversion and output via different output shafts.Dual-clutch transmission is mainly used in manned vehicle, and the problem that existing dual-clutch transmission exists is that axial length is longer, can not adapt to the more and more higher compactedness requirement of manned vehicle, has reduced the car load flexible arrangement.In addition, existing dual-clutch transmission driving device uses 1 retaining driving gear simultaneously as the driving gear that reverses gear, i.e. 1 retaining and the shared same clutch transmits power that reverses gear.Two problems have appearred in this arrangement structure: problem one is under the frequent operating mode of switching 1 retaining and reversing gear of needs, for example moves the storehouse, will increase the loss of 1 retaining, the place power-transfer clutch that reverses gear, and reduces power-transfer clutch service life; Problem two is to make car load increase when starting to walk from 2 retainings to fall 1 retaining process or direct 2 retaining startings that it is dangerous that this has sauntered after having caused the prolongation of gearshift pick-up time and may having produced uphill starting.
The utility model content
The axial length that existing dual-clutch transmission exists is long, amount of parts is many in order to solve, fitting process complicated problems more, and the utility model provides a kind of new construction dual-clutch transmission driving device.
The utility model realizes that the technical solution of above-mentioned purpose is as follows:
A kind of double-clutch speed changer driving device comprises the interior input shaft 1 and outer input shaft 2, first output shaft 3, second output shaft 4 of coaxial setting, and layout is parallel to each other, describedly establish gear respectively on each, also comprise first clutch C1 and second clutch C2, one end of first clutch C1 and interior input shaft 1 is connected, one end of second clutch C2 and outer input shaft 2 is connected, and first clutch C1 and second clutch C2 are positioned at same input end.
Be fixed with a retaining driving gear 11 in described on the input shaft 1 successively and three retaining driving gears, 13, three retaining driving gears also are used as five retaining driving gears simultaneously;
Be fixed with four retaining driving gears 24 on the described outer input shaft 2 successively and two retaining driving gears 22, four retaining driving gears also are used as six retaining driving gears simultaneously, two retaining driving gears also are used as the driving gear that reverses gear simultaneously;
Be provided with a retaining driven gear 31, three retaining driven gears 33, four retaining driven gears 34 on described first output shaft 3 successively, the driven gear 37 and first output gear 30 reverse gear; Wherein a retaining driven gear 31, three retaining driven gears 33, four retaining driven gears 34, driven gear 37 skies that reverse gear are enclosed within on first output shaft 3, and can rotate around first output shaft 3; First output gear 30 is captiveed joint with first output shaft 3, is used for exporting the moment of torsion of first output shaft 3; On first output shaft 3 between a retaining driven gear 31 and the three retaining driven gears 33, be fixed with the first synchro SC1, optionally the first retaining moment of torsion and the 3rd retaining moment of torsion passed to first output shaft 3; On four retaining driven gears 34 and first output shaft 3 between the driven gear 37 of reversing gear, be fixed with the second synchro SC2, optionally the 3rd retaining moment of torsion and the moment of torsion that reverses gear passed to first output shaft 3; Be fixed with Parking ratchet 39 on first output shaft 3 in a described retaining driven gear 31 outsides;
Be parallel to first output shaft 3 and be provided with reverse gear shaft 5, reverse gear shaft 5 skies are arranged with reverse idle gear 57;
An one retaining driving gear 11 and a retaining driven gear 31 are constant-mesh; Three retaining driving gears 13 and three retaining driven gears 33 are constant-mesh; Four retaining driving gears 24 and four retaining driven gears 34 are constant-mesh; Two retaining driving gears 22 are constant-mesh with reverse idle gear 57; Reverse idle gear 57 is constant-mesh with the driven gear 37 that reverses gear simultaneously;
Be provided with five retaining driven gears 45, six retaining driven gears 46 and the two retaining driven gear 42 and second output gears 40 on described second output shaft 4 successively, wherein five retaining driven gears 45, six retaining driven gears 46 and two retaining driven gears, 42 skies are enclosed within on second output shaft 4, and can rotate around second output shaft 4; Second output gear 40 is captiveed joint with second output shaft 4, is used for exporting the moment of torsion of second output shaft 4; Be fixed with the 4th synchro SC4 on second output shaft 4 in five retaining driven gears, 45 outsides; Be fixed with the 3rd synchro SC3 on second output shaft 4 between six retaining driven gears 46 and the two retaining driven gears 42, optionally the 6th retaining moment of torsion and the second retaining moment of torsion passed to second output shaft 4;
Three retaining driving gears 13 and three retaining driven gears 33, five retaining driven gears 45 are constant-mesh; Four retaining driving gears 24 are constant-mesh with four retaining driven gears 34, six retaining driven gears 46 simultaneously; Two retaining driving gears 22 and two retaining driven gears 42 are constant-mesh.
Useful technique effect of the present utility model embodies in the following areas:
1, the utility model is shared three, five retaining driving gears 13, shared four, six retaining driving gears 24, also shared two, driving gear 22 reverses gear, make axial length shorter, can shorten more than the axial length 20mm, be under the situation of 270Nm at certain vehicle transfer torque, and the actual axial length of dual-clutch transmission driving device reaches 235mm, highly beneficial to preceding horizontal manned vehicle layout, meet the manned vehicle demand for development.
2, the utility model is provided with independent reverse idle gear 57, and and two retaining driving gears 22 (simultaneously as reversing gear driving gear), the driven gear constant-mesh that reverses gear form and reverse gear, increased the flexibility that two retainings and the speed ratio that reverses gear are adjusted, help dwindling the distance between shafts between first output shaft 3 and second output shaft 4, reduce the weight and the oad of dual-clutch transmission assembly;
3, the double clutch transmissions that provided of the utility model patent arranged apart has improved life of clutch with a retaining with reversing gear on different power-transfer clutchs, improved pairing device change-speed box starting performance;
4, Parking ratchet 39 is arranged on first output shaft 3 near the high order end position of bearings, compares the Parking ratchet is arranged in structure on the diff, has reduced the requirement of strength and the oad of halting mechanism.
In a word by structural development, axial length of the present utility model is shorter, amount of parts still less, fitting process is simpler, more help improving life of clutch, more help car load Starting Control and safety.
Description of drawings
Fig. 1 is the utility model structural representation;
Fig. 2 is the lateral plan of Fig. 1.
The specific embodiment
Below in conjunction with accompanying drawing, the utility model is further described.
Embodiment:
Referring to Fig. 1, a kind of double-clutch speed changer driving device comprises the interior input shaft 1 and outer input shaft 2, first output shaft 3, second output shaft 4 of coaxial setting, and the layout that is parallel to each other, and above-mentioned four axles are arranged in parallel; Also comprise first clutch C1 and second clutch C2, an end of first clutch C1 and interior input shaft 1 is connected, and an end of second clutch C2 and outer input shaft 2 is connected, and first clutch C1 and second clutch C2 are positioned at same input end.
Be installed with a retaining driving gear 11 on the interior input shaft 1 successively and three retaining driving gears 13, three retaining driving gears also are used as five retaining driving gears simultaneously.
Be installed with four retaining driving gears 24 on the outer input shaft 2 successively and two retaining driving gears 22, four retaining driving gears also are used as six retaining driving gears simultaneously, two retaining driving gears also are used as the driving gear that reverses gear simultaneously.
Be provided with a retaining driven gear 31, three retaining driven gears 33, four retaining driven gears 34 on first output shaft 3 successively, the driven gear 37 and first output gear 30 reverse gear; Wherein a retaining driven gear 31, three retaining driven gears 33, four retaining driven gears 34, driven gear 37 skies that reverse gear are enclosed within on first output shaft 3, and can rotate around first output shaft 3; First output gear 30 is captiveed joint with first output shaft 3, is used for exporting the moment of torsion of first output shaft 3; On first output shaft 3 between a retaining driven gear 31 and the three retaining driven gears 33, be installed with the first synchro SC1, optionally the first retaining moment of torsion and the 3rd retaining moment of torsion passed to first output shaft 3; On four retaining driven gears 34 and first output shaft 3 between the driven gear 37 of reversing gear, be installed with the second synchro SC2, optionally the 3rd retaining moment of torsion and the moment of torsion that reverses gear passed to first output shaft 3; Be installed with Parking ratchet 39 on first output shaft 3 in a described retaining driven gear 31 outsides.
Be parallel to first output shaft 3 and be provided with reverse gear shaft 5, reverse gear shaft 5 skies are arranged with reverse idle gear 57.
An one retaining driving gear 11 and a retaining driven gear 31 are constant-mesh; Three retaining driving gears 13 and three retaining driven gears 33 are constant-mesh; Four retaining driving gears 24 and four retaining driven gears 34 are constant-mesh; Two retaining driving gears 22 are constant-mesh with reverse idle gear 57; Reverse idle gear 57 is constant-mesh with the driven gear 37 that reverses gear simultaneously.
Be provided with five retaining driven gears 45, six retaining driven gears 46 and the two retaining driven gear 42 and second output gears 40 on second output shaft 4 successively, wherein five retaining driven gears 45, six retaining driven gears 46 and two retaining driven gears, 42 skies are enclosed within on first output shaft 3, and can rotate around second output shaft 4; Second output gear 40 is captiveed joint with second output shaft 4, is used for exporting the moment of torsion of second output shaft 4; Be installed with the 4th synchro SC4 on second output shaft 4 in five retaining driven gears, 45 outsides; Be installed with the 3rd synchro SC3 on second output shaft 4 between six retaining driven gears 46 and the two retaining driven gears 42, optionally the 6th retaining moment of torsion and the second retaining moment of torsion passed to second output shaft 4.
Three retaining driving gears 13 and three retaining driven gears 33, five retaining driven gears 45 are constant-mesh; Four retaining driving gears 24 are constant-mesh with four retaining driven gears 34, six retaining driven gears 46 simultaneously; Two retaining driving gears 22 and two retaining driven gears 42 are constant-mesh.
The diff master of diff 6 subtracts gear 60 and meshes with first output gear 30, second output gear 40 respectively, see Fig. 2, Fig. 2 has shown the spatial relation between the interior input shaft 1 of the utility model double clutch transmissions and outer input shaft 2, first output shaft 3 and second output shaft 4, reverse gear shaft 5 and the diff 6.
The power transmission line explanation:
One retaining power transmission line: the first synchro SC1 and a retaining driven gear 31 combinations, first clutch C1 closure, input shaft 1 in engine torque passes to by first clutch C1, retaining driving gear 11 and via constant-mesh keeps off driven gear 31, the first synchro SC1, transfer torque to first output shaft 3, subtract gear 60 by the first defeated gear 30 and diff master again moment of torsion is passed to diff 6, and finally by diff 6 outputting powers.
Two retaining power transmission lines: the 3rd synchro SC3 and 42 combinations of two retaining driven gears, second clutch C2 closure, engine torque passes to outer input shaft 2 by second clutch C2, two retaining driving gears 22 and two via constant-mesh keep off driven gears 42, the 3rd synchro SC3, transfer torque to second output shaft 4, subtract gear 60 by the second defeated gear 40 and diff master again moment of torsion is passed to diff 6, and finally by diff 6 outputting powers.
Three retaining power transmission lines: the first synchro SC1 and 33 combinations of three retaining driven gears, first clutch C1 closure, input shaft 1 in engine torque passes to by first clutch C1, three retaining driving gears 13 and three via constant-mesh keep off driven gears 33, the first synchro SC1, transfer torque to first output shaft 3, subtract gear 60 by the first defeated gear 30 and diff master again moment of torsion is passed to diff 6, and finally by diff 6 outputting powers.
Four retaining power transmission lines: the second synchro SC2 and 34 combinations of four retaining driven gears, second clutch C2 closure, engine torque passes to outer input shaft 2 by second clutch C2, four retaining driving gears 24 and four via constant-mesh keep off driven gears 34, the second synchro SC2, transfer torque to first output shaft 3, subtract gear 60 by the first defeated gear 30 and diff master again moment of torsion is passed to diff 6, and finally by diff 6 outputting powers.
Five retaining power transmission lines: the 4th synchro SC4 and 45 combinations of five retaining driven gears, first clutch C1 closure, input shaft 1 in engine torque passes to by first clutch C1, keep off driven gears 45, the 4th synchro SC4 via constant-mesh five retaining driving gears 13 and five, transfer torque to second output shaft 4, subtract gear 60 by the second defeated gear 40 and diff master again moment of torsion is passed to diff 6, and finally by diff 6 outputting powers.
Six retaining power transmission lines: the 3rd synchro SC3 and 46 combinations of six retaining driven gears, second clutch C2 closure, engine torque passes to outer input shaft 2 by second clutch C2, six retaining driving gears 24 and six via constant-mesh keep off driven gears 46, the 3rd synchro SC3, transfer torque to second output shaft 4, subtract gear 60 by the second defeated gear 40 and diff master again moment of torsion is passed to diff 6, and finally by diff 6 outputting powers.
Transfer route reverses gear: the second synchro SC2 and driven gear 37 combinations of reversing gear, second clutch C2 closure, engine torque passes to outer input shaft 2 by second clutch C2, via constant-mesh two the retaining driving gear 22 (being the driving gear that reverses gear simultaneously), idle gears 57, driven gear 37, the second synchro SC2, first output shaft 3 reverse gear, subtract gear 60 by the first defeated gear 30 and diff master again moment of torsion is passed to diff 6, see Fig. 2, finally by the diff outputting power.
The shift process casehistory:
One keeps off the process that shifts into second: dual-clutch transmission is in a retaining, the first synchro SC1 and a retaining driven gear 31 combinations, and first clutch C1 closure, second clutch C2 opens; The dual-clutch transmission control system is sent one and is kept off the instruction that shifts into second, the gearshift actuating unit is in advance with the 3rd synchro SC3 and 42 combinations of two retaining driven gears, this moment, second clutch C2 still was in open mode, i.e. the second clutch C2 and second output shaft 4 transferring power not; Along with shift process continues, first clutch C1 opens gradually, and meanwhile, second clutch C2 is closed gradually, and this process torque break can not occur; First clutch C1 opens fully, after the complete closure of second clutch C2, first synchro SC1 disengagement combines with a retaining driven gear 31, finish shift process, engine torque subtracts gear 60, is finally exported by diff 6 via second clutch C2, outer input shaft 2, two retaining driving gears 22, two retaining driven gears 42, the 3rd synchro SC3, second output shaft, 4, the second defeated gear 40, diff master.
Claims (1)
1. double-clutch speed changer driving device, comprise the interior input shaft (1) of coaxial setting and outer input shaft (2), first output shaft (3), second output shaft (4), and layout is parallel to each other, describedly establish gear respectively on each, also comprise first clutch (C1) and second clutch (C2), first clutch (C1) is connected with an end of interior input shaft (1), second clutch (C2) is connected with an end of outer input shaft (2), first clutch (C1) and second clutch (C2) are positioned at same input end, it is characterized in that:
Be fixed with a retaining driving gear (11) and three retaining driving gears (13) in described on the input shaft (1) successively, three retaining driving gears also are used as five retaining driving gears simultaneously;
Be fixed with four retaining driving gears (24) and two retaining driving gears (22) on the described outer input shaft (2) successively, four retaining driving gears also are used as six retaining driving gears simultaneously, and two retaining driving gears also are used as the driving gear that reverses gear simultaneously;
Be provided with a retaining driven gear (31), three retaining driven gears (33), four retaining driven gear (34), the driven gear that reverses gear (37) and first output gears (30) on described first output shaft (3) successively; Wherein a retaining driven gear (31), three retaining driven gears (33), four retaining driven gears (34), the driven gear that reverses gear (37) sky are enclosed within on first output shaft (3), and can rotate around first output shaft (3); First output gear (30) is captiveed joint with first output shaft (3), is used for exporting the moment of torsion of first output shaft (3); On first output shaft (3) between a retaining driven gear (31) and the three retaining driven gears (33), be fixed with first synchro (SC1), optionally the first retaining moment of torsion and the 3rd retaining moment of torsion passed to first output shaft (3); On first output shaft (3) between four retaining driven gears (34) and the driven gear that reverses gear (37), be fixed with second synchro (SC2), optionally the 3rd retaining moment of torsion and the moment of torsion that reverses gear passed to first output shaft (3); Be fixed with Parking ratchet (39) on first output shaft (3) in described retaining driven gear (a 31) outside;
Be parallel to first output shaft (3) and be provided with reverse gear shaft (5), reverse gear shaft (5) sky is arranged with reverse idle gear (57);
One retaining driving gear (11) is a constant-mesh with a retaining driven gear (31); Three retaining driving gears (13) and three retaining driven gears (33) are constant-mesh; Four retaining driving gears (24) and four retaining driven gears (34) are constant-mesh; Two retaining driving gears (22) are constant-mesh with reverse idle gear (57); Reverse idle gear (57) is a constant-mesh with the driven gear that reverses gear (37) simultaneously;
Be provided with five retaining driven gears (45), six retaining driven gears (46) and two retaining driven gear (42) and second output gears (40) on described second output shaft (4) successively, wherein five retaining driven gears (45), six retaining driven gears (46) and two retaining driven gear (42) skies are enclosed within on second output shaft (4), and can rotate around second output shaft (4); Second output gear (40) is captiveed joint with second output shaft (4), is used for exporting the moment of torsion of second output shaft (4); Be fixed with the 4th synchro (SC4) on second output shaft (4) in five retaining driven gear (45) outsides; Be fixed with the 3rd synchro (SC3) on second output shaft (4) between six retaining driven gears (46) and the two retaining driven gears (42), optionally the 6th retaining moment of torsion and the second retaining moment of torsion passed to second output shaft (4);
Three retaining driving gears (13) are constant-mesh with three retaining driven gears (33), five retaining driven gears (45); Four retaining driving gears (24) are constant-mesh with four retaining driven gears (34), six retaining driven gears (46) simultaneously; Two retaining driving gears (22) are constant-mesh with two retaining driven gears (42).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205517257U CN201841948U (en) | 2010-09-28 | 2010-09-28 | Dual clutch transmission driver |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205517257U CN201841948U (en) | 2010-09-28 | 2010-09-28 | Dual clutch transmission driver |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201841948U true CN201841948U (en) | 2011-05-25 |
Family
ID=44036850
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010205517257U Expired - Lifetime CN201841948U (en) | 2010-09-28 | 2010-09-28 | Dual clutch transmission driver |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201841948U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101975250A (en) * | 2010-09-28 | 2011-02-16 | 安徽江淮汽车股份有限公司 | Transmission device for dual clutch speed changer |
| CN103470699A (en) * | 2013-07-27 | 2013-12-25 | 赵良红 | Double-clutch-transmission drive mechanism |
| CN113227611A (en) * | 2018-12-14 | 2021-08-06 | 采埃孚股份公司 | Six-speed forward-drive transverse dual clutch transmission with third countershaft |
| CN113473837A (en) * | 2019-03-20 | 2021-10-01 | Ls美创有限公司 | Speed change device for agricultural working vehicle |
| CN113685501A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685497A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
-
2010
- 2010-09-28 CN CN2010205517257U patent/CN201841948U/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101975250A (en) * | 2010-09-28 | 2011-02-16 | 安徽江淮汽车股份有限公司 | Transmission device for dual clutch speed changer |
| CN101975250B (en) * | 2010-09-28 | 2012-06-27 | 安徽江淮汽车股份有限公司 | Transmission device for dual clutch speed changer |
| CN103470699A (en) * | 2013-07-27 | 2013-12-25 | 赵良红 | Double-clutch-transmission drive mechanism |
| CN103470699B (en) * | 2013-07-27 | 2017-06-27 | 赵良红 | Double-clutch-transmdriven driven mechanism |
| CN113227611A (en) * | 2018-12-14 | 2021-08-06 | 采埃孚股份公司 | Six-speed forward-drive transverse dual clutch transmission with third countershaft |
| CN113473837A (en) * | 2019-03-20 | 2021-10-01 | Ls美创有限公司 | Speed change device for agricultural working vehicle |
| CN113685501A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685497A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685501B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
| CN113685497B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101975250B (en) | Transmission device for dual clutch speed changer | |
| CN202431850U (en) | Double-clutch transmission | |
| CN102252063B (en) | Transmission device of double-clutch transmission | |
| CN103842690B (en) | Speed change gear | |
| CN201841948U (en) | Dual clutch transmission driver | |
| CN101968104B (en) | Driving device of double-clutch transmission | |
| CN103148175B (en) | Automobile dual-clutch automatic transmission | |
| CN101975251B (en) | Gearing of dual clutch transmission | |
| CN201851606U (en) | Transmission device for dual-clutch speed changer | |
| CN202152833U (en) | Transmission device of double clutch transmission | |
| CN101975252A (en) | Double-clutch gearbox transmission device | |
| CN102678841A (en) | Longitudinal dual clutch automatic transmission device with direct gear | |
| CN202431852U (en) | Double-clutch automatic transmission transmission gear | |
| CN102242796A (en) | Double-clutch transmission actuating device for | |
| CN202152831U (en) | Transmission device of double clutch transmission | |
| CN103758944A (en) | Driving device for dual-clutch transmission | |
| CN203627674U (en) | Twin-clutch automatic transmission | |
| CN102644699A (en) | Longitudinal double-clutch automatic gearbox transmission device with direct gear | |
| CN201851608U (en) | Transmission device of dual-clutch transmission | |
| CN203162010U (en) | Transmission device for dual-clutch transmission | |
| CN202431851U (en) | Driving device for dual clutch transmission | |
| CN202914686U (en) | Seven-speed dual clutch gearbox transmission device | |
| CN103758969A (en) | Driving device for dual-clutch transmission | |
| CN203488640U (en) | Longitudinally arranged double-clutch gearbox transmission device | |
| CN103758970A (en) | Driving device for dual-clutch transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20110525 Effective date of abandoning: 20120627 |