CN103423386B - Six fast transmission device of dual-clutch transmissions - Google Patents
Six fast transmission device of dual-clutch transmissions Download PDFInfo
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- CN103423386B CN103423386B CN201310321291.XA CN201310321291A CN103423386B CN 103423386 B CN103423386 B CN 103423386B CN 201310321291 A CN201310321291 A CN 201310321291A CN 103423386 B CN103423386 B CN 103423386B
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- gear
- double
- synchronizer
- planetary gear
- row
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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
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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
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
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Abstract
The open a kind of six fast transmission device of dual-clutch transmissions of the present invention, comprise first, second double-row planetary gear, one of them double-row planetary gear of two planetary gear train is made up of front two rows planet row, in front planet row, front sun gear is connected with rear planet carrier, often engages synchronizer or clutch and housing fix by first; Rear planet row adopts dual planetary gear structure, and front ring gear is connected with rear gear ring, power by the second synchronizer or the 3rd synchronizer or clutch outer shaft after first be delivered to rear sun gear or after gear ring, and to be exported by front planet carrier; Another double-row planetary gear adopts Simpson gear shift, and front sun gear is connected with rear sun gear and is connected with the second external axle sleeve, and front ring gear is connected with the second jack shaft.The present invention adopts Simpson and novel double-row star to arrange the combination of gear shift, realize more multiple gear ratios gear and reduce transmission dimensions.
Description
Technical field
The present invention relates to automotive transmission technical field, specifically relate to a kind of six fast transmission device of dual-clutch transmissions.
Background technique
Automotive transmission transmission device is different by train pattern used, has axis jointing type speed changer (parallel shaft transmission) and axis rotary speed gear (planetary transmission) two kinds.Single clutch speed changer and double-clutch speed changer can be divided into by the quantity of clutch.The actuating unit of the double-clutch speed changer of current application is parallel shaft transmission, power transmission is divided into two lines, one is odd number shelves transfer routes, two is even number shelves transfer routes, article two, power transmission line connects first, second input shaft respectively by first, second clutch, outputed power by the driving gear on the driven shaft corresponding with two input shafts again, double-clutch speed changer passes through cooperation control and the control of each synchronizer of two clutches, the transmission ratio when not cutting off power can be realized, thus shorten shift time.But parallel-axis type double-clutch speed changer must adopt independent reverse gear shaft and reverse gear.When an employing output shaft, speed changer axial dimension is large; When adopting two output shafts, speed changer radial dimension is large, takes up room large, is unfavorable for the structure layout design of automobile.The double-clutch speed changer of current application, speed ratio changes greatly, and during such gear shift, engine speed changes greatly, and makes the smoothness of automobile poor.
Summary of the invention
The technical problem to be solved in the present invention is, provide a kind of six fast transmission device of dual-clutch transmissions by brand new, structure is more compact, reduces axis and the radial dimension of speed changer, to overcome the deficiencies in the prior art.
For solving the problems of the technologies described above, the technical solution used in the present invention is: six fast transmission device of dual-clutch transmissions, comprise the first input shaft of the first clutch and correspondence, second input shaft of the second clutch and correspondence, multiple synchronizer, output shaft, the sheathed setting of first and second input shaft described, also comprise first, second double-row planetary gear, intermeshing first gear and the second gear and the 3rd gear and the 4th gear; One of them double-row planetary gear of first, second double-row planetary gear described is made up of front two rows planet row, and in front planet row, front sun gear is connected with rear planet carrier, often engages synchronizer or clutch and housing fix by first; Rear planet row adopts dual planetary gear structure, and front ring gear is connected with rear gear ring, power by the second synchronizer or the 3rd synchronizer or clutch outer shaft after first be delivered to rear sun gear or after gear ring, and to be exported by front planet carrier; Another double-row planetary gear of first, second double-row planetary gear described adopts Simpson gear shift, and front sun gear is connected with rear sun gear and is connected with the second external axle sleeve, and front ring gear is connected with the second jack shaft.
Described second double-row planetary gear adopts Simpson gear shift, the front sun gear of described Simpson gear shift is connected with the second jack shaft and the 4th gear, and the front planet carrier of described Simpson gear shift is connected with rear gear ring and the second gear.
Described first often engagement synchronizer to be located at before the first double-row planetary gear first between external axle sleeve and housing, second synchronizer is arranged between the rear gear ring of the first double-row planetary gear and the 3rd synchronizer, after described 3rd synchronizer is arranged on first between external axle sleeve and the second input shaft.
4th synchronizer is arranged between the rear planet carrier of the second double-row planetary gear and the second external axle sleeve, 5th synchronizer is arranged on second of the second double-row planetary gear often between engagement synchronizer and the second external axle sleeve, and second often engages synchronizer is arranged between the second jack shaft of the 4th gear and the second double-row planetary gear.
Described first double-row planetary gear adopts Simpson gear shift, and the second normal engagement synchronizer and the 5th synchronizer are placed on the right side of the first double-row planetary gear.
Described pair of clutch component is placed on the right side of the first double-row planetary gear, and described pair of clutch component and output shaft be not at not homonymy and at same axis.
Described first often engagement synchronizer be placed on the right side of the second double-row planetary gear, two clutch component and output shaft be not at not homonymy and at same axis.
Described output shaft is placed on the left side of the first double-row planetary gear, and two clutch component and output shaft are at not homonymy but on the same axis.
First gear or the second gear engage with main reducing gear driven gear, main reducing gear driven gear connected with differential.
Compared with prior art, the present invention has the following advantages: the present invention is on the basis of existing dual-clutch transmission, by the combination adopting Simpson gear shift and novel double-row star to arrange gear shift, and coordinate two clutches, multiple synchronizer uses, make it both can reach with few gear logarithm realize more the object of multiple gear ratios gear, the shift property of dual-clutch transmission can be realized again, and axis and the radial dimension of speed changer can be reduced, the size of speed changer is controlled, vehicle structure layout design is more flexible, due to can cost of production be reduced.Transmission gear ratio change is simultaneously less, and during such gear shift, engine speed change is less, and gear shift smoothness is improved.
Accompanying drawing explanation
Fig. 1 is the present invention six fast transmission device of dual-clutch transmission first embodiment power-transmitting unit schematic diagram.
Fig. 2 is the power-transmitting unit schematic diagram of second embodiment of the invention.
Fig. 3 is the power-transmitting unit schematic diagram of third embodiment of the invention.
Fig. 4 is the power-transmitting unit schematic diagram of fourth embodiment of the invention.
Fig. 5 is the power-transmitting unit schematic diagram of fifth embodiment of the invention.
Fig. 6 is the structural representation of the output form change of the fast transmission device of dual-clutch transmission of the present invention six.
Embodiment
The present invention first double-row planetary gear and the second double-row planetary gear adopt novel double-row star row's gear shift or Simpson gear shift.Multiple six speed transmission transmission scheme can be obtained by combination.
Below, in conjunction with Figure of description and specific embodiment, technological scheme of the present invention is further described.
First embodiment
See Fig. 1, double clutch of the present invention comprises two clutch component 1 (comprising first clutch 2 and second clutch 3, the first input shaft 4, second input shaft 5 distinguishing corresponding two clutches), the first double-row planetary gear 181, second double-row planetary gear 182, output shaft 6 and multiple synchronizer.First double-row planetary gear and the second double-row planetary gear are with upper and lower structural configuration, first double-row planetary gear adopts novel double-row star row gear shift, second double-row planetary gear adopts Simpson gear shift, first double-row planetary gear comprises first planet row X1 and the second planet row X2, and the second double-row planetary gear comprises third planet row X3 and fourth planet row X4.
Front sun gear 105, the rear planet carrier 106 of the first double-row planetary gear are connected with external axle sleeve before first 115, front ring gear 103 is connected with rear gear ring 107, front planet carrier 102 is connected with the first gear 161, rear planet row X2 adopts dual planetary gear structural type, layman's star-wheel 108 and expert's star-wheel 109 engage each other, and rear sun gear is connected with external axle sleeve 114 after first.
The front sun gear 134 of the second double-row planetary gear is connected with the second jack shaft 143 and the 4th gear 164, and front planet carrier 131 is connected with rear gear ring 136 and the second gear 162.Front sun gear 134 is connected with rear sun gear 139 and is connected with the second external axle sleeve 143, and front ring gear 132 is connected with the second jack shaft 142.
First input shaft 4 the other end is connected with the 3rd gear the 183, three gear 163 and engages with the 4th gear 164, and the first gear 161 engages with the second gear 162, and the second gear 162 is connected with output shaft 6, and output shaft 6 and dual clutch pack 1 are in the same side.
First often engagement synchronizer 101 be located at before the first double-row planetary gear 181 first between external axle sleeve 115 and housing, the second synchronizer (fourth gear synchronizer 112) is arranged between the rear gear ring 107 of the first double-row planetary gear 181 and the 3rd synchronizer (two, six grades of synchronizers 113).After 3rd synchronizer (two, six grades of synchronizers 113) is arranged on first between external axle sleeve 114 and the second input shaft 5.
4th synchronizer (one, third gear synchronizer 138) is arranged between the rear planet carrier 137 of the second double-row planetary gear 182 and the second external axle sleeve 143.5th synchronizer (Five-gear synchronizer 140) is arranged on second of the second double-row planetary gear 182 often between engagement synchronizer 141 and the second external axle sleeve 143.Second often engages synchronizer 141 is arranged between the second jack shaft 142 of the 4th gear 164 and the second double-row planetary gear 182.
The double-clutch speed changer of the present embodiment can realize six fast forward gearss and a fast reverse gear.First double-row planetary gear 181 realizes two, four, six gears and controls.Second double-row planetary gear 182 realizes one, three, five grade and reverse gear manipulation.
As follows in the action of each gear synchronizer and clutch:
During neutral state, as shown in Figure 1, external axle sleeve before first double-row planetary gear first 115 and housing link together and maintain static by the first normal engagement synchronizer 101, second often engages synchronizer 141 links together the second jack shaft 142 of the 4th gear 164 and the second double-row planetary gear 182, one, third gear synchronizer 138 mediates, and fourth gear synchronizer 112 and two, six grades of synchronizers 113 and Five-gear synchronizer 140 are in not jointing state on right side.
One grade: one, third gear synchronizer 138 moves to left, maintained static with housing by the rear planet carrier 137 in the second double-row planetary gear 182, such second double-row planetary gear 182 forms restriction relation.First clutch 2 engages simultaneously.Power passes to the first input shaft the 4, three gear the 163, four gear 164 through first clutch 2, then through the second double-row planetary gear 182 to output shaft.Now second clutch 3 is in separated state, and all the other synchronizers are in position during neutral state.
Second gear: two, six grades of synchronizers 113 move to left, is connected the first rear external axle sleeve 114 with the second input shaft 5, power is input to rear sun gear 110.First clutch 2 is separated, and second clutch 3 engages simultaneously, and power passes to the second input shaft 5 through first clutch 2, through the first double-row planetary gear 182, first gear 161, second gear 162, then is exported by output shaft 6.
Third gear: one, third gear synchronizer 137 moves to right, fixes the second external axle sleeve 143.Second clutch 3 is separated, and first clutch 2 engages, and realizes third gear transmission of power.
Fourth gear: fourth gear synchronizer 112 moves to left, is connected rear gear ring 107 with two, six grades of synchronizers 113.First clutch 2 is separated, and second clutch 3 engages, and realizes fourth gear transmission of power.Power passes to the second input shaft 5 through second clutch 2, through the first double-row planetary gear 181, first gear 161, second gear 162, then is exported by output shaft 8.
Five grades: Five-gear synchronizer 140 moves to left, often engage synchronizer 141 by second and be connected with the second middle axle sleeve 143.Second clutch 3 is separated, and first clutch 2 engages, and realizes five grades of transmission of power.
Six grades: first often engages synchronizer 101 moves to right, and two, six grades of synchronizers 113, fourth gear synchronizers 112 move to left simultaneously.First clutch 2 is separated, and second clutch 3 engages, and realizes six grades of shelves transmission of power.Power passes to the second input shaft 5 through second clutch 2, through the first double-row planetary gear 181, first gear 161, second gear 162, then is exported by output shaft 8.
Reverse gear: second often engagement synchronizer 141 is right, Five-gear synchronizer 140 moves to left, and one, third gear synchronizer 138 moves to left.Second clutch 3 is separated, and first clutch 2 engages, and realizes reverse gear transmission of power.
Double-clutch speed changer in this invention can realize multiple transforming gear pattern:
Order shift mode:
Order upshift, be raised to second gear for one grade, before shifting commands sends, speed changer is in a gear working state.Needing before preparing to implement gearshift moves to left two, six grades of synchronizers 113 is in advance connected external axle sleeve 114 after first with the second input shaft 5, and now first clutch 2 and second clutch 3 are still in respectively and engage and separated state.When control system send shifting commands be raised to second gear by one grade time, all synchronizer hold modes are motionless, first clutch 2 is progressively separated, second clutch 3 progressively engages simultaneously, until first clutch 2 is separated completely, second clutch 3 engages completely, and control one, third gear synchronizer 137 gets back to neutral position, all the other and one grade and the irrelevant synchronizer of second gear are also failure to actuate.Order upshift and the order downshift of other gears are also known by inference in the same way.
Jump shift mode:
Odd gear changes to the jump lifting shelves of even gear, as one grade be raised to fourth gear or five grades drop to second gear etc., even gear changes to the jump lifting shelves of odd gear, as two upshifts drop to third-class to five grades or six grades, its gear changing mode is the same with the controlling method that order upshifts, and can use the same method and know by inference.
Odd gear changes to the jump upshift of odd gear, and rise third gear for one grade, before shifting commands sends, speed changer is in a gear working state.Before preparing to implement gearshift, first clutch 2 is separated, and one, third gear synchronizer 137 first gets back to neutral position, then move to right second of the second double-row planetary gear the middle axle sleeve 143 fixed with housing.First clutch 2 is rejoined, and completes the control that one grade rises third gear.In the process, second clutch 3 is in separated state always, and all the other and one grade and the irrelevant synchronizer of third gear are also failure to actuate.It is the same that odd gear changes to jump that jump lifting shelves that the jump downshift of odd gear and even gear change to even gear and odd gear the change to odd gear controlling method that upshifts, and can use the same method and know by inference.
The setting of each gear velocity ratio by each planet row a value (a equal planet row the ratio of the gear ring number of teeth and the sun gear number of teeth), the velocity ratio a of the first gear 161 and the second gear 162 and the 3rd gear 163 and the 4th gear 164 velocity ratio a set.The first double-row planetary gear is such as established to comprise first planet row X1 and the second planet row X2, the a value that second double-row planetary gear comprises third planet row X3 and fourth planet row X4 is respectively a1.7, a2.0, a1.5, a4.2, a1, a1.25, then obtain each gear velocity ratio shown in table 1, action than level and gear shift executive component.Numerically, the velocity ratio of each gear, comparatively rationally appropriate than level, obtain good gear ratio characteristic.
the action schedule of table 1 gear shift executive component, each shelves transmission are when than level figure
Note: "○" represents that clutch engages or synchronizer action
Second embodiment
See Fig. 2, on the basis of the first embodiment, by the location swap of the first double-row planetary gear and the second double-row planetary gear, second normal engagement synchronizer 141 and Five-gear synchronizer 140 are placed on the right side of the first double-row planetary gear, all the other position of components are constant, power is exported by the output gear 7 be connected with planet carrier 102 before the second double-row planetary gear, and two clutch component 1 and output shaft gear 7 be not in the same side and at same axis.The velocity ratio needing suitably to change the first gear 261 and the second gear 262, the 3rd gear 263 and the 4th gear 264 is set according to gear velocity ratio, and a value of each planet row.Such first double-row planetary gear 181 realizes 1.3.5 and reverse gear, and the second double-row planetary gear 182 realizes 2.4.6 shelves.
3rd embodiment
See Fig. 3, on the basis of the first embodiment, two clutch component 1 is placed on the right side of the first double-row planetary gear, all the other position of components are constant, and two clutch component 1 and output shaft 6 be not at not homonymy and at same axis.The velocity ratio needing suitably to change the first gear 261 and the second gear 262, the 3rd gear 263 and the 4th gear 264 is set according to gear velocity ratio, and a value of each planet row.Such first double-row planetary gear 181 realizes 2.4.6 shelves, and the second double-row planetary gear 182 realizes 1.3.5 and reverse gear.
4th embodiment
See Fig. 4, on the basis of the 3rd embodiment, by the location swap of the first double-row planetary gear and the second double-row planetary gear, and often engage first the right side that synchronizer 101 is placed on the second double-row planetary gear, all the other position of components are constant, and two clutch component 1 and output shaft 6 be not at not homonymy and at same axis.The velocity ratio needing suitably to change the first gear 261 and the second gear 262, the 3rd gear 263 and the 4th gear 264 is set according to gear velocity ratio, and a value of each planet row.Such first double-row planetary gear 181 realizes 1.3.5 and reverse gear, and the second double-row planetary gear 182 realizes 2.4.6 shelves.
5th embodiment
See Fig. 5, on the basis of the 4th embodiment, output shaft 6 is placed on the left side of the first double-row planetary gear, all the other position of components are constant, and two clutch component 1 and output shaft 6 are at not homonymy but at same axis.The velocity ratio needing suitably to change the first gear 261 and the second gear 262, the 3rd gear 263 and the 4th gear 264 is set according to gear velocity ratio, and a value of each planet row.Such first double-row planetary gear 181 realizes 1.3.5 and reverse gear, and the second double-row planetary gear 182 realizes 2.4.6 shelves.
In addition, in all transmission modes, two clutch component and the output form of output shaft in the same side can suitably change, see Fig. 6, reduce the first gear 161 and the second gear 162 diameter, two gears directly engage with main reducing gear driven gear 190, and by differential mechanism 191 externally outputting power.
Claims (5)
1. six fast transmission device of dual-clutch transmissions, comprise the first input shaft of the first clutch and correspondence, second input shaft of the second clutch and correspondence, multiple synchronizer, output shaft, described first input shaft and the sheathed setting of described second input shaft, also comprise the first double-row planetary gear, the second double-row planetary gear, intermeshing first gear and the second gear and the 3rd gear and the 4th gear; It is characterized in that: one of them double-row planetary gear of described first double-row planetary gear and described second double-row planetary gear is made up of front two rows planet row, in front planet row, front sun gear is connected with rear planet carrier, and by first, often engagement synchronizer and housing are fixed; Rear planet row adopts dual planetary gear structure, and front ring gear is connected with rear gear ring, power by the second synchronizer or the 3rd synchronizer external axle sleeve after first be delivered to rear sun gear or after gear ring, and to be exported by front planet carrier;
Another double-row planetary gear of first, second double-row planetary gear described adopts Simpson gear shift, and front sun gear is connected with rear sun gear and is connected with the second external axle sleeve, and front ring gear is connected with the second jack shaft;
Described second double-row planetary gear adopts Simpson gear shift, the front sun gear of described Simpson gear shift is connected with the second jack shaft and the 4th gear, and the front planet carrier of described Simpson gear shift is connected with rear gear ring and the second gear;
Described first often engagement synchronizer to be located at before the first double-row planetary gear first between external axle sleeve and housing, second synchronizer is arranged between the rear gear ring of the first double-row planetary gear and the 3rd synchronizer, after described 3rd synchronizer is arranged on first between external axle sleeve and the second input shaft;
The power of the first double-row planetary gear is via the first gear, the second gear transmission to output shaft, and the 3rd gear and the 4th gears meshing, give the second double-row planetary gear the transmission of power of the first input shaft.
2. six fast transmission device of dual-clutch transmissions according to claim 1, it is characterized in that: the 4th synchronizer is arranged between the rear planet carrier of the second double-row planetary gear and the second external axle sleeve, 5th synchronizer is arranged on second of the second double-row planetary gear often between engagement synchronizer and the second external axle sleeve, and second often engages synchronizer is arranged between the second jack shaft of the 4th gear and the second double-row planetary gear.
3. six fast transmission device of dual-clutch transmissions according to claim 1, is characterized in that: described first often engagement synchronizer be placed on the right side of the second double-row planetary gear, two clutch component and output shaft be not at not homonymy and at same axis.
4. six fast transmission device of dual-clutch transmissions according to claim 1, is characterized in that: described output shaft is placed on the left side of the first double-row planetary gear, and two clutch component and output shaft are at not homonymy but on the same axis.
5., according to the arbitrary six described fast transmission device of dual-clutch transmissions of Claims 1-4, it is characterized in that: the first gear or the second gear engage with main reducing gear driven gear, main reducing gear driven gear connected with differential.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310321291.XA CN103423386B (en) | 2013-07-27 | 2013-07-27 | Six fast transmission device of dual-clutch transmissions |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310321291.XA CN103423386B (en) | 2013-07-27 | 2013-07-27 | Six fast transmission device of dual-clutch transmissions |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103423386A CN103423386A (en) | 2013-12-04 |
| CN103423386B true CN103423386B (en) | 2016-01-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310321291.XA Expired - Fee Related CN103423386B (en) | 2013-07-27 | 2013-07-27 | Six fast transmission device of dual-clutch transmissions |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105546098B (en) * | 2016-01-19 | 2017-10-17 | 无锡商业职业技术学院 | A kind of double speed automatic transmissions of clutch six of planetary gear type |
| CN107420451B (en) * | 2017-10-06 | 2018-12-14 | 东莞市松研智达工业设计有限公司 | A kind of double drive clutch |
| CN110259894B (en) * | 2018-03-12 | 2022-07-05 | 上海汽车集团股份有限公司 | Twelve-gear automatic gearbox |
| CN111434949A (en) | 2019-01-11 | 2020-07-21 | 罗灿 | Double-sun-wheel line-speed-variable planetary row speed reducer |
| CN110735892A (en) * | 2019-11-18 | 2020-01-31 | 四川坤成润科技有限公司 | parallel fixed shaft type power shifting gearbox |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5078663A (en) * | 1989-09-16 | 1992-01-07 | Dr. Ing. H.C.F. Porsche Ag | Motor vehicle automatic transmission |
| CN1079809A (en) * | 1992-06-09 | 1993-12-22 | 薛南庆 | Epicycle train regid mechanism |
| CN1746529A (en) * | 2004-09-07 | 2006-03-15 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
| CN101149092A (en) * | 2006-09-20 | 2008-03-26 | 马自达汽车股份有限公司 | Automatic transmission |
| CN102797812A (en) * | 2012-08-23 | 2012-11-28 | 赵良红 | Double-clutch transmission device |
| CN203453402U (en) * | 2013-07-27 | 2014-02-26 | 顺德职业技术学院 | Transmission device for six-speed double-clutch transmission |
-
2013
- 2013-07-27 CN CN201310321291.XA patent/CN103423386B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5078663A (en) * | 1989-09-16 | 1992-01-07 | Dr. Ing. H.C.F. Porsche Ag | Motor vehicle automatic transmission |
| CN1079809A (en) * | 1992-06-09 | 1993-12-22 | 薛南庆 | Epicycle train regid mechanism |
| CN1746529A (en) * | 2004-09-07 | 2006-03-15 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
| CN101149092A (en) * | 2006-09-20 | 2008-03-26 | 马自达汽车股份有限公司 | Automatic transmission |
| CN102797812A (en) * | 2012-08-23 | 2012-11-28 | 赵良红 | Double-clutch transmission device |
| CN203453402U (en) * | 2013-07-27 | 2014-02-26 | 顺德职业技术学院 | Transmission device for six-speed double-clutch transmission |
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