CN204164278U - Eight fast Double-clutch-transmdriven driven mechanism - Google Patents
Eight fast Double-clutch-transmdriven driven mechanism Download PDFInfo
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- CN204164278U CN204164278U CN201420567794.5U CN201420567794U CN204164278U CN 204164278 U CN204164278 U CN 204164278U CN 201420567794 U CN201420567794 U CN 201420567794U CN 204164278 U CN204164278 U CN 204164278U
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Abstract
The utility model discloses a kind of eight fast Double-clutch-transmdriven driven 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 independent most low gear 1 and to keep off and top gear 8 keeps off gear pair, and 1 gear is achieved by the combinations of 2 gears, 3 gears and 4 gears, and 8 gears are achieved, for the layout of other component provides axial space by 5 gears, 6 gears and 7 combinations kept off.Multiple gear shares driving gear, substantially reduces the axial space of gearbox arrangement, by cancelling reverse gear shaft, saves the radial space of speed changer simultaneously.The axial dimension of automobile eight fast 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 eight fast Double-clutch-transmdriven driven 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, forward gear and the gear demand of reversing 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 first gear, rear clutch is connected with second gear, power is passed to gear-box via clutch, through corresponding shift 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 eight fast Double-clutch-transmdriven driven 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 eight fast Double-clutch-transmdriven driven 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, first input shaft is fixedly connected with 2/ to reverse gear driving gear, 4/6 gear driving gear, second input shaft is fixedly connected with 3/5 gear driving gear, 7 gear driving gears, on first output shaft, movable sheath is connected to the driven gear that reverses gear, 4 gear driven gears, 3 gear driven gears, first output shaft is fixedly connected with respectively and to reverse gear driven gear, 4 gear driven gears, the reverse gear synchronizer that 3 gear driven gears are corresponding, 4 gear synchronizers, 3 gear synchronizers, first output shaft is fixedly connected with the first final gear, on second output shaft, movable sheath is connected to 2 gear driven gears, 6 gear driven gears, 5 gear driven gears, 7 gear driven gears, second output shaft is fixedly connected with the second final gear, the second output shaft is fixedly connected with respectively with 2 gear driven gears, 6 gear driven gears, 5 gear driven gears, 7 gear driven gears corresponding 2 gear synchronizers, 6 gear synchronizers, 5 gear synchronizers, 7 gear synchronizers, 3 gear driven gears are fixedly connected with the 3 gear driven synchronizer corresponding with 4 gear driven gears, 5 gear driven gears are fixedly connected with the 5 gear driven synchronizer corresponding with 6 gear driven gears, first final gear and the second final gear are all in transmission connection differential mechanism, 2/ driving gear and 2 that reverses gear keeps off driven gear and engages, the driven gear and 2 that reverses gear keeps off driven gear and engages, 4/6 gear driving gear and 4 keeps off driven gear, 6 gear driven gear engagement driving, 3/5 gear driving gear and 3 keeps off driven gear, 5 gear driven gear engagement driving, 7 gear driving gears and 7 keep off driven gear engagement driving.
The transfer route of 1 gear power is: second clutch input → the second input shaft → 3/5 keeps off driving gear → 3 and keeps off driven gear → 3 and keep off driven synchronizer → 4 and keep off driven gear → 4/6 and keep off driving gear → 2 of reversing gear, driving gear → the first input shaft → 2/ and keep off driven gear → 2 and keep off synchronizer → the second output shaft → the second final gear → differential mechanism and export;
The transfer routes of 2 gear power are: driving gear → 2 of reversing gear, first clutch input the → the first input shaft → 2/ keep off driven gear → 2 and keep off synchronizer → the second output shaft → the second final gear → differential mechanism and export;
The transfer route of 3 gear power is: second clutch input → the second input shaft → 3/5 keeps off gear driven gear → 3, driving gear → 3 gear synchronizer → the first output shaft → the first final gear → differential mechanism and exports;
The transfer route of 4 gear power is: first clutch input → the first input shaft → 4/6 keeps off gear driven gear → 4, driving gear → 4 gear synchronizer → the first output shaft → the first final gear → differential mechanism and exports;
The transfer route of 5 gear power is: second clutch input → the second input shaft → 3/5 keeps off gear driven gear → 5, driving gear → 5 gear synchronizer → the second output shaft → the second final gear → differential mechanism and exports;
The transfer route of 6 gear power is: first clutch input → the first input shaft → 4/6 keeps off gear driven gear → 6, driving gear → 6 gear synchronizer → the second output shaft → the second final gear → differential mechanism and exports;
The transfer route of 7 gear power is: second clutch input → the second input shaft → 7 keep off gear driven gear → 7, driving gear → 7 gear synchronizer → the second output shaft → the second final gear → differential mechanism and export;
8 transfer routes keeping off power are: first clutch input → the first input shaft → 4/6 keeps off gear driven gear → 3/5, gear driven synchronizer → 5, gear driven gear → 5, driving gear → 6 and keeps off the gear synchronizer → the second output shaft → the second final gear → differential mechanism output of gear driven gear → 7, gear driving gear → 7, driving gear → the second input shaft → 7;
Reverse gear the transfer route of power: driving gear → 2 of reversing gear, first clutch input the → the first input shaft → 2/ keep off the driven gear → driven gear that reverses gear → reverse gear synchronizer → the first output shaft → the first final gear → differential mechanism and export;
By two input shafts, the form of two output shafts, the synchronizer of each gear upshift and downshift that can realize double-clutch speed changer is put into gear function in advance.
1 gear speed ratio by numerical value larger 2 gear speed ratios and 3 gear speed ratios be multiplied, then divided by numerical value less 4 gear speed ratios, thus obtain numerical value larger 1 gear speed ratio.
2/ driving gear and 2 that reverses gear keeps off driven gear and often engages, and the driven gear and 2 that reverses gear keeps off driven gear and often engages, and realizes 2 gear transmissions by 2 gear synchronizers on the second output shaft; Reverse gear is realized by the reverse gear synchronizer on the first output shaft;
3/5 gear driving gear and 3 keep off driven gear, 5 and keeps off driven gear and often engage, and realizes 3 gear transmissions and 5 keep off transmissions respectively by 3 synchronizers, 5 effects of working as synchronizer;
4/6 gear driving gear and 4 keep off driven gear, 6 and keep off driven gear and often engage, and respectively by 4 keeping off synchronizers, 6 effects keeping off synchronizers realize 4 gear transmissions and 6 and keep off transmissions;
7 gear driving gears and 7 keep off driven gear and often engage, and realize 7 gear transmissions by 7 gear synchronizers on the second output shaft;
3 gear gear pairs are also as the one-level gear pair of 1 gear, after power is passed to 3 gear driven gears from the second input shaft, transmission of power to 4 is kept off driven gear by the one-way synchronization device being connected to 3 gear driven gears by a solidity, gear pairs are kept off by transmission of power to the first input shaft again by 4, power is passed to 2 gear driven gears from 2 gear gear pairs by the first input shaft, then exported by the second output shaft, the one-way synchronization device utilizing increase like this, in conjunction with 3 gear gear pairs, 4 gear gear pairs and 2 gear gear pairs, thus acquisition 1 gear power transmission line realizes 1 gear transmission.
6 gear gear pairs are also as the one-level gear pair of 8 gears, after power is passed to 6 gear driven gears from the first input shaft, transmission of power to 5 is kept off driven gear by the one-way synchronization device being connected to 6 gear driven gears by a solidity, gear pairs are kept off by transmission of power to the second input shaft again by 5, power is passed to 7 gear driven gears from 7 gear gear pairs by the second input shaft, then outputed power by 7 gear synchronizers on the second output shaft, the one-way synchronization device utilizing increase like this, in conjunction with 5 gear gear pairs, 6 gear gear pairs and 7 gear gear pairs, thus acquisition 8 gear power transmission lines realize 8 gear transmissions, the speed ratio of 8 gears is multiplied with 7 gear speed ratios by the 6 gear speed ratios that numerical value is less, again divided by the 5 gear speed ratios that numerical value is larger, thus obtain 8 less gear speed ratios of numerical value, realize the transmission of power of most high speed gear,
The utility model reduces independent most low gear 1 to be kept off and top gear 8 keeps off gear pair, and 1 gear is achieved by the combinations of 2 gears, 3 gears and 4 gears, and 8 gears are achieved, for the layout of other component provides axial space by 5 gears, 6 gears and 7 combinations kept off.Multiple gear shares driving gear, substantially reduces the axial space of gearbox arrangement, by cancelling reverse gear shaft, saves the radial space of speed changer simultaneously.The axial dimension of automobile eight fast 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, on differential mechanism, fixed cover is connected to differential mechanism gear ring, and the first final gear, the second final gear all engage with differential mechanism gear ring.Differential mechanism passes through differential mechanism gear ring and the first final gear, the second final gear transferring power, compact structure, reliable transmission.
As preferably, reverse gear synchronizer and 4 gear synchronizers are arranged on same synchronizer assembly, 2 gear synchronizers and 6 gear synchronizers are arranged on same synchronizer assembly, 5 gear synchronizers and 7 gear synchronizers are arranged on same synchronizer assembly, reverse gear synchronizer and 4 gear synchronizers are arranged on and reverse gear between driven gear and 4 gear driven gears, 2 gear synchronizers and 6 gear synchronizers are arranged between 2 gear driven gears and 6 gear driven gears, 5 gear synchronizers and 7 gear synchronizers are arranged between 5 gear driven gears and 7 gear driven gears, 3 gear synchronizers are arranged between 3 gear driven gears and the first final gear, the driven synchronizer of 3 gear is arranged between 4 gear driven gears and 3 gear driven gears, the driven synchronizer of 5 gear is arranged between 6 gear driven gears and 5 gear driven gears.2/ reverse gear driving gear, 2 gear driven gears, driven gears that reverse gear are arranged at same plane in the radial direction, and 2/ reverse gear driving gear and the driven gear that reverses gear has gap in radial direction.Vibrational power flow is reasonable, and component are installed compact, 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 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.This vibrational power flow is compacter, takes up room little.
Compared with prior art, the beneficial effects of the utility model are: the axial dimension of the fast double-clutch automatic gearbox driving mechanism of (1) automobile eight is short, and compact structure, takes up room little, can meet the designing requirement of automotive light weight technology, compact type; (2) reduce independent most low gear 1 to keep off and top gear 8 keeps off gear pair, 1 gear is achieved by the combination of 2 gears, 3 gears and 4 gears, 8 gears are achieved by the combination of 5 gears, 6 gears and 7 gears, for the layout of other component provides axial space, by cancelling reverse gear shaft, save the radial space of speed changer simultaneously.Multiple gear shares driving gear, substantially reduces the axial space of gearbox arrangement.
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 gearshift logic diagram of the present utility model;
In figure: 1, first input shaft, 2, second input shaft, 3, first output shaft, 4, second output shaft, 5, differential mechanism, 6, differential mechanism gear ring, 1a, 7 gear driving gears, 2a, 3/5 gear driving gear, 3a, 4/6 gear driving gear, 4a, 2/ reverses gear driving gear, 1b, second final gear, 2b, 7 gear driven gears, 3b, 5 gear driven gears, 4b, 6 gear driven gears, 5b, 2 gear driven gears, 1c, first final gear, 2c, 3 gear driven gears, 3c, 4 gear driven gears, 4c, reverse gear driven gear, a, reverse gear synchronizer, b, 4 gear synchronizers, c, the driven synchronizer of 3 gear, d, 3 gear synchronizers, e, 2 gear synchronizers, f, 6 gear synchronizers, g, the driven synchronizer of 5 gear, h, 5 gear synchronizers, i, 7 gear 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 eight fast Double-clutch-transmdriven driven mechanism (see accompanying drawing 1, accompanying drawing 2), comprise the second input shaft 2, first output shaft 3, second output shaft 4, first input shaft of the first input shaft 1 of first clutch K1 and correspondence, second clutch K2 and correspondence, the second input shaft, the first output shaft, the second output 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.First input shaft is fixedly connected sequentially from left to right and 2/ has reversed gear driving gear 4a, 4/6 gear driving gear 3a, second input shaft has been fixedly connected sequentially from left to right 3/5 gear driving gear 2a, 7 gear driving gear 1a, on first output shaft, movable sheath is connected to the driven gear 4c that reverses gear successively from left to right, 4 gear driven gear 3c, 3 gear driven gear 2c, first output shaft is fixedly connected with respectively and to reverse gear driven gear, 4 gear driven gears, the reverse gear synchronizer a that 3 gear driven gears are corresponding, 4 gear synchronizer b, 3 gear synchronizer d, first output shaft is fixedly connected with the first final gear 1c, on second output shaft, movable sheath is connected to 2 gear driven gear 5b, 6 gear driven gear 4b, 5 gear driven tooth 3b, 7 gear driven gear 2b successively from left to right, second output shaft is fixedly connected with the second final gear 1b, the second output shaft is fixedly connected with respectively with 2 gear driven gears, 6 gear driven gears, 5 gear driven tooth, 2 gear synchronizer e, 6 gear synchronizer f, 5 gear synchronizer h, 7 gear synchronizer i that 7 gear driven gears are corresponding, 3 gear driven gears are fixedly connected with the 3 gear driven synchronizer c corresponding with 4 gear driven gears, 5 gear driven gears are fixedly connected with the 5 gear driven synchronizer g corresponding with 6 gear driven gears, first final gear and the second final gear are all in transmission connection differential mechanism 5, on differential mechanism, fixed cover is connected to differential mechanism gear ring 6, first final gear, the second final gear all engages with differential mechanism gear ring.2/ driving gear and 2 that reverses gear keeps off driven gear and engages, the driven gear and 2 that reverses gear keeps off driven gear and engages, 4/6 gear driving gear and 4 keeps off driven gear, 6 and keeps off driven gear engagement driving, 3/5 gear driving gear and 3 keeps off driven gear, 5 and keeps off driven gear engagement driving, and 7 gear driving gears and 7 keep off driven gear engagement driving.2/ reverses gear, and driving gear, 4/6 keeps off driving gear, 3/5 gear driving gear, 7 keeps off driving gears and sets gradually from left to right, and first clutch is arranged on the right-hand member of the first input shaft, and second clutch is arranged on the right-hand member of the second input shaft.2/ reverse gear driving gear, 2 gear driven gears, driven gears that reverse gear are arranged at same plane in the radial direction, and 2/ reverse gear driving gear and the driven gear that reverses gear has gap in radial direction.Reverse gear synchronizer and 4 gear synchronizers are arranged on same synchronizer assembly, 2 gear synchronizers and 6 gear synchronizers are arranged on same synchronizer assembly, 5 gear synchronizers and 7 gear synchronizers are arranged on same synchronizer assembly, reverse gear synchronizer and 4 gear synchronizers are arranged on and reverse gear between driven gear and 4 gear driven gears, 2 gear synchronizers and 6 gear synchronizers are arranged between 2 gear driven gears and 6 gear driven gears, 5 gear synchronizers and 7 gear synchronizers are arranged between 5 gear driven gears and 7 gear driven gears, 3 gear synchronizers are arranged between 3 gear driven gears and the first final gear, the driven synchronizer of 3 gear is arranged between 4 gear driven gears and 3 gear driven gears, the driven synchronizer of 5 gear is arranged between 6 gear driven gears and 5 gear driven gears.The gearshift 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 gear power G1 is: second clutch input → the second input shaft → 3/5 keeps off driving gear → 3 and keeps off driven gear → 3 and keep off driven synchronizer → 4 and keep off driven gear → 4/6 and keep off driving gear → 2 of reversing gear, driving gear → the first input shaft → 2/ and keep off driven gear → 2 and keep off synchronizer → the second output shaft → the second final gear → differential mechanism and export;
The transfer routes of 2 gear power G2 are: driving gear → 2 of reversing gear, first clutch input the → the first input shaft → 2/ keep off driven gear → 2 and keep off synchronizer → the second output shaft → the second final gear → differential mechanism and export;
The transfer route of 3 gear power G3 is: second clutch input → the second input shaft → 3/5 keeps off gear driven gear → 3, driving gear → 3 gear synchronizer → the first output shaft → the first final gear → differential mechanism and exports;
The transfer route of 4 gear power G4 is: first clutch input → the first input shaft → 4/6 keeps off gear driven gear → 4, driving gear → 4 gear synchronizer → the first output shaft → the first final gear → differential mechanism and exports;
The transfer route of 5 gear power G5 is: second clutch input → the second input shaft → 3/5 keeps off gear driven gear → 5, driving gear → 5 gear synchronizer → the second output shaft → the second final gear → differential mechanism and exports;
The transfer route of 6 gear power G6 is: first clutch input → the first input shaft → 4/6 keeps off gear driven gear → 6, driving gear → 6 gear synchronizer → the second output shaft → the second final gear → differential mechanism and exports;
The transfer route of 7 gear power G7 is: second clutch input → the second input shaft → 7 keep off gear driven gear → 7, driving gear → 7 gear synchronizer → the second output shaft → the second final gear → differential mechanism and export;
8 transfer routes keeping off power G8 are: first clutch input → the first input shaft → 4/6 keeps off gear driven gear → 3/5, gear driven synchronizer → 5, gear driven gear → 5, driving gear → 6 and keeps off the gear synchronizer → the second output shaft → the second final gear → differential mechanism output of gear driven gear → 7, gear driving gear → 7, driving gear → the second input shaft → 7;
Reverse gear the transfer route of power GR: driving gear → 2 of reversing gear, first clutch input the → the first input shaft → 2/ keep off the driven gear → driven gear that reverses gear → reverse gear synchronizer → the first output shaft → the first final gear → differential mechanism and export;
By two input shafts, the form of two output shafts, the synchronizer of each gear upshift and downshift that can realize double-clutch speed changer is put into gear function in advance.
1 gear speed ratio by numerical value larger 2 gear speed ratios and 3 gear speed ratios be multiplied, then divided by numerical value less 4 gear speed ratios, thus obtain numerical value larger 1 gear speed ratio.
2/ driving gear and 2 that reverses gear keeps off driven gear and often engages, and the driven gear and 2 that reverses gear keeps off driven gear and often engages, and realizes 2 gear transmissions by 2 gear synchronizers on the second output shaft; Reverse gear is realized by the reverse gear synchronizer on the first output shaft;
3/5 gear driving gear and 3 keep off driven gear, 5 and keeps off driven gear and often engage, and realizes 3 gear transmissions and 5 keep off transmissions respectively by 3 synchronizers, 5 effects keeping off synchronizers;
4/6 gear driving gear and 4 keep off driven gear, 6 and keep off driven gear and often engage, and respectively by 4 keeping off synchronizers, 6 effects keeping off synchronizers realize 4 gear transmissions and 6 and keep off transmissions;
7 gear driving gears and 7 keep off driven gear and often engage, and realize 7 gear transmissions by 7 gear synchronizers on the second output shaft;
3 gear gear pairs are also as the one-level gear pair of 1 gear, after power is passed to 3 gear driven gears from the second input shaft, transmission of power to 4 is kept off driven gear by the one-way synchronization device being connected to 3 gear driven gears by a solidity, gear pairs are kept off by transmission of power to the first input shaft again by 4, power is passed to 2 gear driven gears from 2 gear gear pairs by the first input shaft, then exported by the second output shaft, the one-way synchronization device utilizing increase like this, in conjunction with 3 gear gear pairs, 4 gear gear pairs and 2 gear gear pairs, thus acquisition 1 gear power transmission line realizes 1 gear transmission.
6 gear gear pairs are also as the one-level gear pair of 8 gears, after power is passed to 6 gear driven gears from the first input shaft, transmission of power to 5 is kept off driven gear by the one-way synchronization device being connected to 6 gear driven gears by a solidity, gear pairs are kept off by transmission of power to the second input shaft again by 5, power is passed to 7 gear driven gears from 7 gear gear pairs by the second input shaft, then outputed power by 7 gear synchronizers on the second output shaft, the one-way synchronization device utilizing increase like this, in conjunction with 5 gear gear pairs, 6 gear gear pairs and 7 gear gear pairs, thus acquisition 8 gear power transmission lines realize 8 gear transmissions, the speed ratio of 8 gears is multiplied with 7 gear speed ratios by the 6 gear speed ratios that numerical value is less, again divided by the 5 gear speed ratios that numerical value is larger, thus obtain 8 less gear speed ratios of numerical value, realize the transmission of power of most high speed gear,
The utility model reduces independent most low gear 1 to be kept off and top gear 8 keeps off gear pair, and 1 gear is achieved by the combinations of 2 gears, 3 gears and 4 gears, and 8 gears are achieved, for the layout of other component provides axial space by 5 gears, 6 gears and 7 combinations kept off.Multiple gear shares driving gear, substantially reduces the axial space of gearbox arrangement, by cancelling reverse gear shaft, saves the radial space of speed changer simultaneously.The axial dimension of automobile eight fast 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 (6)
1. a fast Double-clutch-transmdriven driven 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, first input shaft is fixedly connected with 2/ to reverse gear driving gear, 4/6 gear driving gear, second input shaft is fixedly connected with 3/5 gear driving gear, 7 gear driving gears, on first output shaft, movable sheath is connected to the driven gear that reverses gear, 4 gear driven gears, 3 gear driven gears, first output shaft is fixedly connected with respectively and to reverse gear driven gear, 4 gear driven gears, the reverse gear synchronizer that 3 gear driven gears are corresponding, 4 gear synchronizers, 3 gear synchronizers, first output shaft is fixedly connected with the first final gear, on second output shaft, movable sheath is connected to 2 gear driven gears, 6 gear driven gears, 5 gear driven gears, 7 gear driven gears, second output shaft is fixedly connected with the second final gear, the second output shaft is fixedly connected with respectively with 2 gear driven gears, 6 gear driven gears, 5 gear driven gears, 7 gear driven gears corresponding 2 gear synchronizers, 6 gear synchronizers, 5 gear synchronizers, 7 gear synchronizers, 3 gear driven gears are fixedly connected with the 3 gear driven synchronizer corresponding with 4 gear driven gears, 5 gear driven gears are fixedly connected with the 5 gear driven synchronizer corresponding with 6 gear driven gears, first final gear and the second final gear are all in transmission connection differential mechanism, 2/ driving gear and 2 that reverses gear keeps off driven gear and engages, the driven gear and 2 that reverses gear keeps off driven gear and engages, 4/6 gear driving gear and 4 keeps off driven gear, 6 gear driven gear engagement driving, 3/5 gear driving gear and 3 keeps off driven gear, 5 gear driven gear engagement driving, 7 gear driving gears and 7 keep off driven gear engagement driving.
2. eight fast Double-clutch-transmdriven driven mechanism according to claim 1, it is characterized in that, on differential mechanism, fixed cover is connected to differential mechanism gear ring, and the first final gear, the second final gear all engage with differential mechanism gear ring.
3. eight fast Double-clutch-transmdriven driven mechanism according to claim 1, it is characterized in that, reverse gear synchronizer and 4 gear synchronizers are arranged on same synchronizer assembly, 2 gear synchronizers and 6 gear synchronizers are arranged on same synchronizer assembly, 5 gear synchronizers and 7 gear synchronizers are arranged on same synchronizer assembly, reverse gear synchronizer and 4 gear synchronizers are arranged on and reverse gear between driven gear and 4 gear driven gears, 2 gear synchronizers and 6 gear synchronizers are arranged between 2 gear driven gears and 6 gear driven gears, 5 gear synchronizers and 7 gear synchronizers are arranged between 5 gear driven gears and 7 gear driven gears, 3 gear synchronizers are arranged between 3 gear driven gears and the first final gear, the driven synchronizer of 3 gear is arranged between 4 gear driven gears and 3 gear driven gears, the driven synchronizer of 5 gear is arranged between 6 gear driven gears and 5 gear driven gears.
4. eight fast Double-clutch-transmdriven driven mechanism according to claim 1 or 2 or 3, it is characterized in that, 2/ reverse gear driving gear, 2 gear driven gears, driven gears that reverse gear are arranged at same plane in the radial direction, and 2/ reverse gear driving gear and the driven gear that reverses gear has gap in radial direction.
5. eight fast Double-clutch-transmdriven driven mechanism according to claim 1 or 2 or 3, is characterized in that, the first input shaft, the second input shaft, the first output shaft, the second output shaft be arranged in parallel.
6. eight fast Double-clutch-transmdriven driven mechanism according to claim 1 or 2 or 3, is characterized in that, the 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420567794.5U CN204164278U (en) | 2014-09-29 | 2014-09-29 | Eight fast Double-clutch-transmdriven driven mechanism |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420567794.5U CN204164278U (en) | 2014-09-29 | 2014-09-29 | Eight fast Double-clutch-transmdriven driven mechanism |
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| CN204164278U true CN204164278U (en) | 2015-02-18 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE202016101867U1 (en) | 2016-04-08 | 2017-07-12 | Hofer Forschungs- Und Entwicklungs Gmbh | Dual-clutch transmission and hybrid powertrain with a dual-clutch transmission |
-
2014
- 2014-09-29 CN CN201420567794.5U patent/CN204164278U/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE202016101867U1 (en) | 2016-04-08 | 2017-07-12 | Hofer Forschungs- Und Entwicklungs Gmbh | Dual-clutch transmission and hybrid powertrain with a dual-clutch transmission |
| WO2017174741A1 (en) | 2016-04-08 | 2017-10-12 | Hofer Powertrain Uk Limited | Dual clutch transmission and hybridized drive train having a dual clutch transmission |
| US11371587B2 (en) | 2016-04-08 | 2022-06-28 | Mclaren Automotive Limited | Compact gearbox and e-reverse |
| US11401999B2 (en) | 2016-04-08 | 2022-08-02 | Mclaren Automotive Limited | Dual clutch transmission and hybridized drive train having a dual clutch transmission |
| US11754147B2 (en) | 2016-04-08 | 2023-09-12 | Mclaren Automotive Limited | Compact gearbox and e-reverse |
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