CN204226569U - Automobile double clutch automatic gearbox driving mechanism - Google Patents
Automobile double clutch automatic gearbox driving mechanism Download PDFInfo
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- CN204226569U CN204226569U CN201420568087.8U CN201420568087U CN204226569U CN 204226569 U CN204226569 U CN 204226569U CN 201420568087 U CN201420568087 U CN 201420568087U CN 204226569 U CN204226569 U CN 204226569U
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- 230000005540 biological transmission Effects 0.000 claims description 35
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- 238000012546 transfer Methods 0.000 description 16
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Abstract
The utility model discloses a kind of automobile double clutch automatic gearbox driving mechanism, be intended to solve existing gearing actuator axial dimension longer, structure is compact not, takes up room large, can not meet the deficiency of designing requirement of automotive light weight technology, compact type.This model utility reduces the most high-grade independent 7 grades of gear pairs, and 7 grades are achieved, for the layout of other component provides axial space by the combination of 5 grades, 6 grades and 2 grades.Multiple gear shares driving gear, substantially reduces the axial space of gearbox arrangement.5 synchronizer assemblies are utilized to achieve 7 forward gears and 1 reverse gear.The axial dimension of automobile double clutch automatic gearbox driving mechanism is short, and compact structure takes up room little, can meet the designing requirement of automotive light weight technology, compact type.
Description
Technical field
The utility model relates to a kind of gearing actuator, and more particularly, it relates to a kind of automobile double clutch automatic gearbox driving mechanism of compact structure.
Background technique
The development of current automotive industry, energy-saving and emission-reduction become the Main way of design, and car load is got over strict for the designing requirement of speed changer, therefore have high efficiency, high-comfort double-clutch automatic gearbox becomes development trend gradually.Powertrain arrangement in double-clutch automatic gearbox is the important component part of whole speed changer, is also the most important condition of follow-up design on hardware and software, and therefore double-clutch speed changer requires also more and more higher to the layout of transmission scheme.In order to improve power character and the Economy of car load, lightweight becomes a developing direction of speed changer, and therefore requiring gearing actuator need be more and more compacter, to meet the arrangement requirement of car load.In the transmission system of existing most of double-clutch speed changer, 7 advance gears of seven speed dual clutch transmission and the gear demand of 1 reverse gear are mostly could be realized by the gear pair of more group of quantity, axial dimension is longer, and consider that preposition forerunner's automobile is generally all subject to the restriction of very limited axial space layout, this will ask the axial dimension of speed changer transmission scheme shorter, therefore axially shorter dual-clutch transmission transmission scheme is designed, the radial space of speed changer can be saved further, make speed changer compacter.
Chinese patent notification number CN201531590U, disclose a kind of automobile double clutch type automatic gearbox transmission device, primarily of double clutch assembly, front and back clutch actuating mechanism and speed-change gear box composition, before double clutch assembly comprises, rear clutch, front and back clutch is by front, rear clutch actuating mechanism controls to engage front clutch respectively and is separated rear clutch, or clutch separation front clutch after engaging, front clutch is connected with one grade of gear, rear clutch is connected with intermediate gear, power is passed to gear-box via clutch, through corresponding shifting gear, power is finally delivered to differential assembly outputting power, double clutch housing is driven by power source.By controlling the overlap in conjunction with speed and combination of two clutches thus realizing power gear shifting process, ensure the continuity of transmission of power, but transmission shaft is to longer dimension, structure is compact not, take up room large, the designing requirement of automotive light weight technology, compact type can not be met.
Model utility content
It is longer that the utility model overcomes existing gearing actuator axial dimension, structure is compact not, take up room large, the deficiency of designing requirement of automotive light weight technology, compact type can not be met, provide a kind of automobile double clutch automatic gearbox driving mechanism, its axial dimension is short, compact structure, take up room little, the designing requirement of automotive light weight technology, compact type can be met.
In order to solve the problems of the technologies described above, the utility model is by the following technical solutions: a kind of automobile double clutch automatic gearbox driving mechanism, comprise the first input shaft of first clutch and correspondence, second input shaft of second clutch and correspondence, first output shaft, second output shaft, reverse gear shaft, first input shaft is fixedly connected with 1/reverse driving gear, 3/5 grade of driving gear, second input shaft is fixedly connected with 2 grades of driving gears, 4/6 grade of driving gear, on first output shaft, movable sheath is connected to 1 grade of driven gear, 5 grades of driven gears, 2 grades of driven gears, 6 grades of driven gears, first output shaft is fixedly connected with respectively with 1 grade of driven gear, 5 grades of driven gears, 2 grades of driven gears, 1 grade of synchronizer that 6 grades of driven gears are corresponding, 5 grades of synchronizers, 2 grades of synchronizers, 6 grades of synchronizers, first output shaft is fixedly connected with the first final gear, 2 grades of driven gears are fixedly connected with the 2 grade driven synchronizers corresponding with 5 grades of driven gears, on second output shaft, movable sheath is connected to 3 grades of driven gears, reverse gear driven gear, 4 grades of driven gears, second output shaft is fixedly connected with the second final gear, the second output shaft is fixedly connected with respectively with 3 grades of driven gears, reverse gear driven gear, 3 grades of synchronizers, reversing-gear synchronizer, 4 grades of synchronizers that 4 grades of driven gears are corresponding, reverse gear shaft is fixedly connected with reverse gear one-level driven gear, reverse gear secondary driving gear, first final gear and the second final gear are all in transmission connection differential mechanism, 1/reverse driving gear and 1 grade of driven gear, reverse gear one-level driven gear engagement driving, 3/5 grade of driving gear and 3 grades of driven gears, 5 grades of driven gear engagement driving, 2 grades of driving gears and 2 grades of driven gear engagement driving, 4/6 grade of driving gear and 4 grades of driven gear, 6 grades of driven gear engagement driving, reverse gear secondary driving gear and reverse gear driven gear engagement driving.
The transfer route of 1 grade of power is: first clutch input the → the first grade driven gear → 1, reverse driving gear → 1, input shaft → 1/ grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of 2 grades of power is: second clutch input grade driven gear → 2, grade driving gear → 2, the → the second input shaft → 2 grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of 3 grades of power is: first clutch input grade driven gear → 3, grade driving gear → 3, the → the first input shaft → 3/5 grade synchronizer → the second output shaft → the second final gear → differential mechanism exports;
The transfer route of 4 grades of power is: second clutch input grade driven gear → 4, grade driving gear → 4, the → the second input shaft → 4/6 grade synchronizer → the second output shaft → the second final gear → differential mechanism exports;
The transfer route of 5 grades of power is: first clutch input grade driven gear → 5, grade driving gear → 5, the → the first input shaft → 3/5 grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of 6 grades of power is: second clutch input grade driven gear → 6, grade driving gear → 6, the → the second input shaft → 4/6 grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of 7 grades of power is: first clutch input grade grade driven gear → 2, driven synchronizer → 2, grade driven gear → 2, grade driving gear → 5, the → the first input shaft → 3/5 grade grade driven gear → 6, grade driving gear → 6, driving gear → the second input shaft → 4/6 grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of reverse gear power: first clutch input the → the first input shaft → 1/ reverse driving gear → reverse gear one-level driven gear → reverse gear shaft → reverse gear secondary driving gear → reverse gear driven gear → reversing-gear synchronizer → the second output shaft → the second final gear → differential mechanism exports;
By two input shafts, two output shafts, odd number shelves and reverse gear are arranged on the first input shaft by the form of a reverse gear shaft, and even number shelves are arranged on the second input shaft, can realize each gear upshift of double-clutch speed changer and the pre-engage a gear function of synchronizer of downshift.
1/ reverse driving gear often engages with 1 grade of driven gear, reverse gear one-level driven gear, realizes 1 grade of transmission by grade synchronizer of 1 on the first output shaft;
Reverse gear one-level driven gear drives reverse gear secondary driving gear to rotate, and reverse gear secondary driving gear often engages with the reverse gear driven gear of the second output shaft, realizes reverse gear by the reversing-gear synchronizer on the second output shaft;
2 grades of driving gears often engage with 2 grades of driven gears, realize 2 grades of transmissions by grade synchronizer of 2 on the first output shaft;
3/5 grade of driving gear often engages with 3 grades of driven gears, 5 grades of driven gears, realizes 3 grades of transmissions and 5 grades of transmissions respectively by 3 synchronizers, 5 effects of working as synchronizer;
4/6 grade of driving gear often engages with 4 grades of driven gears, 6 grades of driven gears, and the effect respectively by 4 grades of synchronizers, 6 grades of synchronizers realizes 4 grades of transmissions and 6 grades of transmissions;
5 grades of gear pairs are also as the one-level gear pair of 7 grades, after power is passed to 5 grades of driven gears from the first input shaft, the 2 grades of driven synchronizers being fixedly connected 2 grades of driven gears by one are by transmission of power to 2 grade driven gear, pass through 2 grades of gear pairs again by transmission of power to the second input shaft, power is passed to 6 grades of driven gears from 6 grades of gear pairs by the second input shaft, then outputed power by grade synchronizer of 6 on the first output shaft, 2 grades of driven synchronizers utilizing increase like this, in conjunction with 5 grades of gear pairs, 2 grades of gear pairs and 6 grades of gear pairs, thus acquisition 7 grades of power transmission lines realize 7 grades of transmissions, the speed ratio of 7 grades is multiplied with 6 grades of speed ratios by 5 grades of speed ratios that numerical value is less, again divided by 2 grades of speed ratios that numerical value is larger, thus obtain 7 grades of less speed ratios of numerical value, realize the transmission of power of most high gear,
The utility model reduces the most high-grade independent 7 grades of gear pairs, and 7 grades are achieved, for the layout of other component provides axial space by the combination of 5 grades, 6 grades and 2 grades.Multiple gear shares driving gear, substantially reduces the axial space of gearbox arrangement, and the utility model utilizes 5 synchronizer assemblies to achieve 7 forward gears and 1 reverse gear.The axial dimension of automobile double clutch automatic gearbox driving mechanism is short, and compact structure takes up room little, can meet the designing requirement of automotive light weight technology, compact type.
As preferably, the first input shaft, the second input shaft, the first output shaft, the second output shaft, reverse gear shaft be arranged in parallel.First input shaft is actively socketed in the second input shaft.This vibrational power flow is compacter, takes up room little.
As preferably, 1/ reverse driving gear, 1 grade of driven gear, reverse gear one-level driven gear three gears are in same radial plane.2 grades of driving gears and 2 grades of driven gears are in same radial plane; In radial directions, gap is equipped with between 2 grades of driving gears and reverse gear secondary driving gear, between 2 grades of driving gears and reverse gear driven gear, between 2 grades of driven gears and reverse gear driven gear.Vibrational power flow is reasonable, and component are installed compact, meet the designing requirement of automotive light weight technology, compact type.
Compared with prior art, the beneficial effects of the utility model are: the axial dimension of (1) automobile double clutch automatic gearbox driving mechanism is short, and compact structure, takes up room little, can meet the designing requirement of automotive light weight technology, compact type; (2) reduce the most high-grade independent 7 grades of gear pairs, 7 grades are achieved, for the layout of other component provides axial space by the combination of 5 grades, 6 grades and 2 grades.
Accompanying drawing explanation
Fig. 1 is a kind of structural representation of the present utility model;
Fig. 2 is side view of the present utility model;
Fig. 3 is shift logic figure of the present utility model;
In figure: 1, first input shaft, 2, second input shaft, 3, first output shaft, 4, second output shaft, 5, reverse gear shaft, 6, differential mechanism, 1a, 4/6 grade of driving gear, 2a, 2 grades of driving gears, 3a, 3/5 grade of driving gear, 4a, 1/ reverse driving gear, 1b, first final gear, 2b, 6 grades of driven gears, 3b, 2 grades of driven gears, 4b, 5 grades of driven gears, 5b, 1 grade of driven gear, 1c, second final gear, 2c, 4 grades of driven gears, 3c, reverse gear driven gear, 4c, 3 grades of driven gears, 1d, reverse gear shaft reverse gear secondary driving gear, 2d, reverse gear shaft reverse gear one-level driven gear, a, 1 grade of synchronizer, b, 5 grades of synchronizers, c, 2 grades of driven synchronizers, d, 2 grades of synchronizers, e, 6 grades of synchronizers, f, 3 grades of synchronizers, g, reversing-gear synchronizer, h, 4 grades of synchronizers, K1, first clutch, K2, second clutch.
Embodiment
Below by specific embodiment, and by reference to the accompanying drawings, the technical solution of the utility model is further described specifically:
Embodiment: a kind of automobile double clutch automatic gearbox driving mechanism (see accompanying drawing 1, accompanying drawing 2), comprise the second input shaft 2, first output shaft 3, second output shaft 4, the reverse gear shaft 5 of the first input shaft 1 of first clutch K1 and correspondence, second clutch K2 and correspondence, first clutch is connected to the right-hand member of the first input shaft, and second clutch is connected to the right-hand member of the second input shaft.First input shaft has been fixedly connected sequentially from left to right 1/reverse driving gear 4a, 3/5 grade of driving gear 3a, second input shaft has been fixedly connected sequentially from left to right 2 grades of driving gear 2a, 4/6 grade of driving gear 1a, on first output shaft, movable sheath is connected to 1 grade of driven gear 5b successively from left to right, 5 grades of driven gear 4b, 2 grades of driven gear 3b, 6 grades of driven gear 2b, first output shaft is fixedly connected with respectively with 1 grade of driven gear, 5 grades of driven gears, 2 grades of driven gears, 1 grade of synchronizer a that 6 grades of driven gears are corresponding, 5 grades of synchronizer b, 2 grades of synchronizer d, 6 grades of synchronizer e, on first output shaft, right-hand member is fixedly connected with the first final gear 1b, 2 grades of driven gears are fixedly connected with the 2 grade driven synchronizer cs corresponding with 5 grades of driven gears, on second output shaft, movable sheath is connected to 3 grades of driven gear 4c, reverse gear driven gear 3c, 4 grades of driven gear 2c successively from left to right, on second output shaft, right-hand member is fixedly connected with the second final gear 1c, the second output shaft is fixedly connected with respectively with 3 grades of driven gears, reverse gear driven gear, 3 grades of synchronizer f, the reversing-gear synchronizer g that 4 grades of driven gears are corresponding, 4 grades of synchronizer h, reverse gear one-level that reverse gear shaft has been fixedly connected sequentially from left to right driven gear 2d, reverse gear secondary driving gear 1d, first final gear and the second final gear are all in transmission connection differential mechanism 6,1/reverse driving gear and 1 grade of driven gear, reverse gear one-level driven gear engagement driving, 3/5 grade of driving gear and 3 grades of driven gears, 5 grades of driven gear engagement driving, 2 grades of driving gears and 2 grades of driven gear engagement driving, 4/6 grade of driving gear and 4 grades of driven gear, 6 grades of driven gear engagement driving, reverse gear secondary driving gear and reverse gear driven gear engagement driving.First input shaft, the second input shaft, the first output shaft, the second output shaft, reverse gear shaft be arranged in parallel.First input shaft is actively socketed in the second input shaft, and the left end of the first input shaft stretches out the second input shaft left end.1/ reverse driving gear, 1 grade of driven gear, reverse gear one-level driven gear three gears are in same radial plane.2 grades of driving gears and 2 grades of driven gears are in same radial plane; In radial directions, gap is equipped with between 2 grades of driving gears and reverse gear secondary driving gear, between 2 grades of driving gears and reverse gear driven gear, between 2 grades of driven gears and reverse gear driven gear.1 grade of synchronizer and 5 grades of synchronizers are arranged on same synchronizer assembly, and 2 grades of synchronizers and 6 grades of synchronizers are arranged on same synchronizer assembly, and reversing-gear synchronizer and 4 grades of synchronizers are arranged on same synchronizer assembly.1 grade of synchronizer and 5 grades of synchronizers are arranged between 1 grade of driven gear and 5 grades of driven gears, 2 grades of synchronizers and 6 grades of synchronizers are arranged between 2 grades of driven gears and 6 grades of driven gears, reversing-gear synchronizer and 4 grades of synchronizers are arranged between reverse gear driven gear and 4 grades of driven gears, 2 grades of driven synchronizers are arranged between 5 grades of driven gears and 2 grades of driven gears, and 3 grades of synchronizers are arranged on the left of 3 grades of driven gears.The shift logic of each gear is see shown in accompanying drawing 3.The power transmission line of each gear is as follows:
The transfer route of 1 grade of power G1 is: first clutch input the → the first grade driven gear → 1, reverse driving gear → 1, input shaft → 1/ grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of 2 grades of power G2 is: second clutch input grade driven gear → 2, grade driving gear → 2, the → the second input shaft → 2 grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of 3 grades of power G3 is: first clutch input grade driven gear → 3, grade driving gear → 3, the → the first input shaft → 3/5 grade synchronizer → the second output shaft → the second final gear → differential mechanism exports;
The transfer route of 4 grades of power G4 is: second clutch input grade driven gear → 4, grade driving gear → 4, the → the second input shaft → 4/6 grade synchronizer → the second output shaft → the second final gear → differential mechanism exports;
The transfer route of 5 grades of power G5 is: first clutch input grade driven gear → 5, grade driving gear → 5, the → the first input shaft → 3/5 grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of 6 grades of power G6 is: second clutch input grade driven gear → 6, grade driving gear → 6, the → the second input shaft → 4/6 grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of 7 grades of power G7 is: first clutch input grade grade driven gear → 2, driven synchronizer → 2, grade driven gear → 2, grade driving gear → 5, the → the first input shaft → 3/5 grade grade driven gear → 6, grade driving gear → 6, driving gear → the second input shaft → 4/6 grade synchronizer → the first output shaft → the first final gear → differential mechanism exports;
The transfer route of reverse gear power GR: first clutch input the → the first input shaft → 1/ reverse driving gear → reverse gear one-level driven gear → reverse gear shaft → reverse gear secondary driving gear → reverse gear driven gear → reversing-gear synchronizer → the second output shaft → the second final gear → differential mechanism exports;
By two input shafts, two output shafts, odd number shelves and reverse gear are arranged on the first input shaft by the form of a reverse gear shaft, and even number shelves are arranged on the second input shaft, can realize each gear upshift of double-clutch speed changer and the pre-engage a gear function of synchronizer of downshift.
1/ reverse driving gear often engages with 1 grade of driven gear, reverse gear one-level driven gear, realizes 1 grade of transmission by grade synchronizer of 1 on the first output shaft;
Reverse gear one-level driven gear drives reverse gear secondary driving gear to rotate, and reverse gear secondary driving gear often engages with the reverse gear driven gear of the second output shaft, realizes reverse gear by the reversing-gear synchronizer on the second output shaft;
2 grades of driving gears often engage with 2 grades of driven gears, realize 2 grades of transmissions by grade synchronizer of 2 on the first output shaft;
3/5 grade of driving gear often engages with 3 grades of driven gears, 5 grades of driven gears, realizes 3 grades of transmissions and 5 grades of transmissions respectively by 3 synchronizers, 5 effects of working as synchronizer;
4/6 grade of driving gear often engages with 4 grades of driven gears, 6 grades of driven gears, and the effect respectively by 4 grades of synchronizers, 6 grades of synchronizers realizes 4 grades of transmissions and 6 grades of transmissions;
5 grades of gear pairs are also as the one-level gear pair of 7 grades, after power is passed to 5 grades of driven gears from the first input shaft, 2 grades of driven synchronizers of 2 grades of driven gears are connected to by transmission of power to 2 grade driven gear by a solidity, pass through 2 grades of gear pairs again by transmission of power to the second input shaft, power is passed to 6 grades of driven gears from 6 grades of gear pairs by the second input shaft, then outputed power by grade synchronizer of 6 on the first output shaft, 2 grades of driven synchronizers utilizing increase like this, in conjunction with 5 grades of gear pairs, 2 grades of gear pairs and 6 grades of gear pairs, thus acquisition 7 grades of power transmission lines realize 7 grades of transmissions, the speed ratio of 7 grades is multiplied with 6 grades of speed ratios by 5 grades of speed ratios that numerical value is less, again divided by 2 grades of speed ratios that numerical value is larger, thus obtain 7 grades of less speed ratios of numerical value, realize the transmission of power of most high gear,
The utility model reduces the most high-grade independent 7 grades of gear pairs, and 7 grades are achieved, for the layout of other component provides axial space by the combination of 5 grades, 6 grades and 2 grades.Multiple gear shares driving gear, substantially reduces the axial space of gearbox arrangement, and the utility model utilizes 5 synchronizer assemblies to achieve 7 forward gears and 1 reverse gear.The axial dimension of automobile double clutch automatic gearbox driving mechanism is short, and compact structure takes up room little, can meet the designing requirement of automotive light weight technology, compact type.
Above-described embodiment is one of the present utility model preferably scheme, not does any pro forma restriction to the utility model, also has other variant and remodeling under the prerequisite not exceeding the technological scheme described in claim.
Claims (5)
1. an automobile double clutch automatic gearbox driving mechanism, it is characterized in that, comprise the first input shaft of first clutch and correspondence, second input shaft of second clutch and correspondence, first output shaft, second output shaft, reverse gear shaft, first input shaft is fixedly connected with 1/reverse driving gear, 3/5 grade of driving gear, second input shaft is fixedly connected with 2 grades of driving gears, 4/6 grade of driving gear, on first output shaft, movable sheath is connected to 1 grade of driven gear, 5 grades of driven gears, 2 grades of driven gears, 6 grades of driven gears, first output shaft is fixedly connected with respectively with 1 grade of driven gear, 5 grades of driven gears, 2 grades of driven gears, 1 grade of synchronizer that 6 grades of driven gears are corresponding, 5 grades of synchronizers, 2 grades of synchronizers, 6 grades of synchronizers, first output shaft is fixedly connected with the first final gear, 2 grades of driven gears are fixedly connected with the 2 grade driven synchronizers corresponding with 5 grades of driven gears, on second output shaft, movable sheath is connected to 3 grades of driven gears, reverse gear driven gear, 4 grades of driven gears, second output shaft is fixedly connected with the second final gear, the second output shaft is fixedly connected with respectively with 3 grades of driven gears, reverse gear driven gear, 3 grades of synchronizers, reversing-gear synchronizer, 4 grades of synchronizers that 4 grades of driven gears are corresponding, reverse gear shaft is fixedly connected with reverse gear one-level driven gear, reverse gear secondary driving gear, first final gear and the second final gear are all in transmission connection differential mechanism, 1/reverse driving gear and 1 grade of driven gear, reverse gear one-level driven gear engagement driving, 3/5 grade of driving gear and 3 grades of driven gears, 5 grades of driven gear engagement driving, 2 grades of driving gears and 2 grades of driven gear engagement driving, 4/6 grade of driving gear and 4 grades of driven gear, 6 grades of driven gear engagement driving, reverse gear secondary driving gear and reverse gear driven gear engagement driving.
2. automobile double clutch automatic gearbox driving mechanism according to claim 1, is characterized in that, the first input shaft, the second input shaft, the first output shaft, the second output shaft, reverse gear shaft be arranged in parallel.
3. automobile double clutch automatic gearbox driving mechanism according to claim 1, it is characterized in that, the first input shaft is actively socketed in the second input shaft.
4. the automobile double clutch automatic gearbox driving mechanism according to claim 1 or 2 or 3, is characterized in that, 1/ reverse driving gear, 1 grade of driven gear, reverse gear one-level driven gear three gears are in same radial plane.
5. the automobile double clutch automatic gearbox driving mechanism according to claim 1 or 2 or 3, is characterized in that, 2 grades of driving gears and 2 grades of driven gears are in same radial plane; In radial directions, gap is equipped with between 2 grades of driving gears and reverse gear secondary driving gear, between 2 grades of driving gears and reverse gear driven gear, between 2 grades of driven gears and reverse gear driven gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420568087.8U CN204226569U (en) | 2014-09-29 | 2014-09-29 | Automobile double clutch automatic gearbox driving mechanism |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420568087.8U CN204226569U (en) | 2014-09-29 | 2014-09-29 | Automobile double clutch automatic gearbox driving mechanism |
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| CN204226569U true CN204226569U (en) | 2015-03-25 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201420568087.8U Expired - Fee Related CN204226569U (en) | 2014-09-29 | 2014-09-29 | Automobile double clutch automatic gearbox driving mechanism |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107524764A (en) * | 2016-06-20 | 2017-12-29 | 格特拉格有限两合公司 | Dual-clutch transmission with bridge-type clutch |
| CN107917167A (en) * | 2016-10-09 | 2018-04-17 | 昆山德拉特兰传动科技有限公司 | Eight fast double-clutch automatic gearboxes |
| WO2020125507A1 (en) * | 2018-12-20 | 2020-06-25 | Ningbo Geely Automobile Research & Development Co., Ltd. | A transmission for a vehicle |
-
2014
- 2014-09-29 CN CN201420568087.8U patent/CN204226569U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107524764A (en) * | 2016-06-20 | 2017-12-29 | 格特拉格有限两合公司 | Dual-clutch transmission with bridge-type clutch |
| CN107917167A (en) * | 2016-10-09 | 2018-04-17 | 昆山德拉特兰传动科技有限公司 | Eight fast double-clutch automatic gearboxes |
| WO2020125507A1 (en) * | 2018-12-20 | 2020-06-25 | Ningbo Geely Automobile Research & Development Co., Ltd. | A transmission for a vehicle |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150325 |
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| CF01 | Termination of patent right due to non-payment of annual fee |