CN104373524A - Eight-speed double-clutch type automatic transmission - Google Patents
Eight-speed double-clutch type automatic transmission Download PDFInfo
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- CN104373524A CN104373524A CN201410363137.3A CN201410363137A CN104373524A CN 104373524 A CN104373524 A CN 104373524A CN 201410363137 A CN201410363137 A CN 201410363137A CN 104373524 A CN104373524 A CN 104373524A
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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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention discloses an eight-speed double-clutch type automatic transmission comprising a first input shaft, a second input shaft, a first output shaft, a second output shaft, a first automatic clutch and a second automatic clutch, wherein the first input shaft and the second input shaft are connected in a sleeved mode, and the first output shaft and the second output shaft are parallel to the first input shaft and the second input shaft. A third-gear and fifth-gear driving gear and a seventh-gear driving gear are fixedly arranged on the first input shaft. A fourth-gear and sixth-gear driving gear and a second-back-gear driving gear are fixedly arranged on the second input shaft. A second-gear driven gear, a third-gear driven gear and a fourth-gear driven gear are arranged on the first output shaft in a sleeving mode. A fifth-gear driven gear, a sixth-gear driven gear and a back-gear driven gear meshed with the second-gear driven gear are arranged on the second output shaft in a sleeving mode. A fourth-gear driven gear synchronizer capable of being connected with the third-gear driven gear is arranged on the fourth-gear driven gear, a sixth-gear driven gear synchronizer capable of being connected with the fifth-gear driven gear is arranged on the sixth-gear driven gear, and therefore the third-gear and fifth-gear driving gear and the fourth-gear and sixth-gear driving gear can be used for transmitting the power of a first gear and an eighth gear. The eight-speed double-clutch type automatic transmission is small in axial length, compact in structure, suitable for a front-engine front-drive saloon car, and convenient to distribute.
Description
Technical field
The present invention relates to a kind of transmission for vehicle, particularly a kind of eight speed double-clutch formula automatic transmission being applicable to preposition forerunner's car.
Background technique
Along with the development of automotive industry, there is high efficiency, high-comfort double-clutch automatic gearbox becomes development trend gradually.Existing eight speed double-clutch formula automatic transmission are integrated in a gearbox by two gearboxes and two clutches, two input shafts connected together rotationally are connected with one of them clutch respectively, two input shafts transmit the power of two gearbox speed groups respectively, by automatically switching between two clutches thus completing gearshift program, therefore the power shfit of gearshift procedure can be realized, namely power is interrupted at gearshift procedure, the power of motor can be delivered to wheel all the time, gear shift is steady rapidly, not only ensure that the acceleration of vehicle, and no longer produce the abrupt deceleration situation because gear shift causes due to vehicle, also the travelling comfort of vehicle operating is improved greatly.
Such as, a kind of in Chinese patent literature disclosed " double-clutch automatic transmission ", its publication No. is CN101713459A, comprise the housing of speed changer, first, second input shaft the and optionally rotation of motor is passed to the first automatic clutch and second automatic clutch of the first or second input shaft, first output shaft substantially parallel with it and the second output shaft is provided with in the first and second input shaft both sides, be located at driving gear on input shaft be socketed in rotationally the first output shaft and/: or the driven gear on the second output shaft gnaws conjunction mutually, being located in the driving gear on the first and second input shafts at least respectively has driving gear we closes mutually with the driven gear of two on the first and second output shafts simultaneously.Above-mentioned double-clutch automatic transmission, by sharing driving gear, makes the arrangement of gear transmission group become parallel arrangement, therefore can shorten the axial length of speed changer, thus make its structure more compact.
The length of gearbox is mainly determined by the quantity of the driving gear of axially-aligned on input shaft, on the one hand, because the highest in this type of eight speed double-clutch formula automatic transmission and minimum two gears are all adopt one-level gear pair, and carry out transmission of power by synchronizer, therefore, the power of motor is all the driven gear be delivered to by a driving gear on a wherein input shaft on a wherein output shaft, recycle a synchronizer and make corresponding output shaft and this driven gear synchronous axial system, and correspondingly outputting power, the driving gear corresponding with the highest of speed changer and lowest gear is just merely for the transmission of power of a gear, thus be unfavorable for the quantity reducing driving gear.Secondly, owing at most just engaging for a pair two simply with two driven gears on the first output shaft and the second output shaft and direct outputting power in remaining driving gear on input shaft simultaneously, that is, each gear is all be directly passed to output shaft by the synchronizer of corresponding gear by the driving gear on input shaft again to after primary transmission simple between the driven gear of on output shaft, therefore, a driving gear at most can only simultaneously for the transmission of power of two gears, and then make the quantity of driving gear at least need to maintain six, thus make the axial dimension of whole speed changer still partially long, its layout on preposition forerunner's car is subject to certain restrictions, and be unfavorable for the lightweight of car.
Summary of the invention
The present invention is that the mission case axial length existing for the eight speed double-clutch formula automatic transmission in order to solve prior art is longer, the problem that layout on preposition forerunner's car is restricted, provides the eight speed double-clutch formula automatic transmission that a kind of axial length is short, compact structure is conveniently arranged.
To achieve these goals, the present invention is by the following technical solutions:
A kind of eight speed double-clutch formula automatic transmission, comprise differential mechanism, first input shaft, second input shaft the and optionally rotation of motor passed to the first automatic clutch of the first input shaft and optionally the rotation of engine crankshaft passed to the second automatic clutch of the second input shaft, second input shaft rotationally coaxial sleeve is connected on the first input shaft, first input shaft stretches out in the second input shaft away from engine crankshaft one end, first output shaft parallel with the second input shaft with the first input shaft and the second output shaft is provided with the second input shaft both sides at the first input shaft, first output shaft is installed with the first final gear engaged with the gear ring of differential mechanism, second output shaft is installed with the second final gear engaged with the gear ring of differential mechanism, the second half section stretching out in the second input shaft at the first input shaft is installed with three or five grades of driving gears near engine crankshaft one end, second input shaft keeps off driving gear and two reverse driving gears near three or five grades of driving gear one end to being installed with four or six successively near engine crankshaft one end, first output shaft is arranged with third gear driven gear rotationally that engage with three or five grades of driving gears, the fourth gear driven gear that driving gear engages is kept off with four or six, the second gear driven gear engaged with two reverse driving gears, first output shaft is also provided with corresponding third gear synchronizer, fourth gear synchronizer and second gear synchronizer, second output shaft is arranged with five grades of driven gears rotationally that engage with three or five grades of driving gears, six grades of driven gears that driving gear engages are kept off with four or six, the reverse gear driven gear engaged with second gear driven gear, second output shaft is also provided with corresponding Five-gear synchronizer, six grades of synchronizers and reversing-gear synchronizer, fourth gear driven gear is provided with the fourth gear driven gear synchronizer that can engage with third gear driven gear.
Present invention eliminates one grade of driving gear in existing eight speed double-clutch formula automatic transmission, the fourth gear driven gear synchronizer that can be combined with third gear driven gear is set simultaneously on fourth gear driven gear, like this, when wheel is with one grade of starting, first automatic clutch combines and the first input shaft is rotated, namely three or five grades of driving gears on first input shaft drive the third gear driven gear on the first output shaft to rotate, now, fourth gear driven gear synchronizer is engaged with third gear driven gear, fourth gear driven gear is combined and synchronous axial system with third gear driven gear, and then oppositely drive four or six grades of driving gears on the second input shaft to rotate, like this, two reverse driving gears be installed on the second input shaft rotate, and drive the second gear driven gear on the first output shaft to rotate, engage second gear synchronizer, the first output shaft rotation can be driven, and by the first final gear, differential mechanism outputting power.Meanwhile, three or five grades of driving gears are by the third gear driven gear engaged with it, five grades of driven gears, and corresponding third gear synchronizer and Five-gear synchronizer still normally can transmit third gear, the power of five grades, four or six gear driving gears are by the fourth gear driven gear engaged with it, six grades of driven gears, and corresponding fourth gear synchronizer and six grades of synchronizers still normally can transmit fourth gear, the power of six grades.That is, the present invention is by increase fourth gear driven gear synchronizer, make three or five grades of driving gears can simultaneously as the driving gear of three gears, therefore the quantity of driving gear and corresponding driven gear can be reduced, and fourth gear driven gear synchronizer is arranged on three, between fourth gear driven gear, without the need to increasing the axial length of retarder, thus effectively shorten the axial length of whole retarder, simplify the structure simultaneously, make the overall structure of gearbox more compact.
As preferably, the first input shaft is installed with seven grades of driving gears, the second output shaft is then arranged with rotationally the seven grades of driven gears be meshed with seven grades of driving gears, the second output shaft is also provided with corresponding seven grades of synchronizers.The power of such motor can be delivered on the second output shaft by seven grades of driving gears, seven grades of driven gears, seven grades of synchronizers, and be outputted on wheel by the second final gear, differential mechanism by the first input shaft.
As preferably, six grades of driven gears are provided with six grades of driven gear synchronizers that can engage with five grades of driven gears, like this, the present invention is when transmission eight grades of power, second automatic clutch combines and the second input shaft is rotated, namely four or six grades of driving gears on second input shaft drive six grades of driven gears on the second output shaft to rotate, now, six grades of driven gear synchronizers are engaged with five grades of driven gears, five grades of driven gears are combined and synchronous axial system with six grades of driven gears, and then oppositely drive three or five grades of driving gears on the first input shaft to rotate, like this, the seven grades of driving gears be installed on the first input shaft rotate, and drive seven grades of driven gears on the second output shaft to rotate, engage seven grades of synchronizers, the second output shaft rotation can be driven, and by the second final gear, differential mechanism outputting power.That is, the present invention is by increase by six grades of driven gear synchronizers, make four or six grades of driving gears can simultaneously as the driving gear of three gears, therefore the quantity of corresponding eight grades of driving gears and corresponding driven gear can be reduced, thus further shorten the axial length of whole retarder, make the overall structure of gearbox more simple and compact simultaneously.
As preferably, described first output shaft is installed with parking ratchet wheel, described parking ratchet wheel and seven grades of driving gears are positioned at same cross section.
In existing double-clutch automatic transmission, parking ratchet wheel is arranged on differential mechanism, thus needs to take certain cabinet space.And parking ratchet wheel is arranged on the first output shaft by the present invention, and with seven grades of driving gears are positioned at same cross section, because seven grades of driving gear positions corresponding on the first output shaft have unnecessary space, therefore can not increase the axial length of speed changer, the cabinet space also not outside occupying volume.In addition, because parking ratchet wheel much smaller than the moment of torsion of differential mechanism, therefore, will be arranged on the first output shaft by the moment of torsion of the first output shaft, be conducive to reducing parking braking power, thus reduce boundary dimension and the requirement of strength of halting mechanism.
Therefore, the present invention has following beneficial effect: axial length is short, compact structure, be applicable to preposition forerunner's car, and arranges that it is conveniently arranged.
Accompanying drawing explanation
Fig. 1 is structured flowchart of the present invention.
In figure: 1, first input shaft 2, second input shaft 3, first automatic clutch 4, second automatic clutch 5, differential mechanism 51, gear ring 6, bent axle 7, first output shaft 8, second output shaft 9, first final gear 10, second final gear 11, two reverse driving gears 12, three or five grades of driving gears 13, four or six grades of driving gears 14, seven grades of driving gears 15, second gear driven gear 16, third gear driven gear 17, fourth gear driven gear 18, five grades of driven gears 19, six grades of driven gears 20, seven grades of driven gears 21, reverse gear driven gear 22, second gear synchronizer 23, third gear synchronizer 24, fourth gear synchronizer 25, Five-gear synchronizer 26, six grades of synchronizers 27, seven grades of synchronizers 28, reversing-gear synchronizer 29, fourth gear driven gear synchronizer 30, six grades of driven gear synchronizers 31, parking ratchet wheel.
Embodiment
Below in conjunction with accompanying drawing, the present invention will be further described.
In the embodiment shown in fig. 1, a kind of eight speed double-clutch formula automatic transmission of the present invention, comprise the first input shaft 1, coaxial sleeve is connected on the second input shaft 2 on the first input shaft rotationally, for the first automatic clutch 3 of the speed, transmission of odd number shelves, for the second automatic clutch 4 of the speed, transmission of even number shelves and reverse gear and by transmission of power to the differential mechanism 5 of wheel, the active friction plate of the first automatic clutch and the second automatic clutch is connected on the bent axle 6 of motor, the second input shaft is stretched out in one end near engine crankshaft on first input shaft, and be connected with the driven friction disk of the first automatic clutch, one end near engine crankshaft on second input shaft is connected with the driven friction disk of the second automatic clutch, thus make the rotation of engine crankshaft pass to the first input shaft by engaging the first automatic clutch, or engaging the second automatic clutch makes the rotation of engine crankshaft pass to the second input shaft.
First input shaft stretches out in the second input shaft away from one end of engine crankshaft, at the first input shaft, first output shaft 7 and second output shaft 8 parallel with the second input shaft with the first input shaft is set with the second input shaft both sides.First output shaft is fixedly installed first final gear 9 engaged with the gear ring 51 of differential mechanism with outputting power, similarly, second output shaft is fixedly installed second final gear 10 engaged with the gear ring of differential mechanism with outputting power, first, second final gear can be separately positioned on first, second output shaft near engine crankshaft one end, wherein the first output shaft for exporting one, two, three, the power of fourth speed, and the second output shaft is for exporting the power of five, six, seven, eight and reverse speed.
On the second half section stretching out in the second input shaft at the first input shaft from be fixedly installed successively near engine crankshaft one end on three or five grades of driving gears 12 and seven grades of driving gear 14, second input shafts near three or five grades of driving gear one end to being fixedly installed four or six gear driving gear 13 and two reverse driving gears 11 successively near engine crankshaft one end.Meanwhile, corresponding on the first output shaft position be arranged with rotationally engage with three or five grades of driving gears third gear driven gear 16, keep off the fourth gear driven gear 17 that driving gear engages, the second gear driven gear 15 engaged with two reverse driving gears with four or six.In addition, first output shaft also needs arrange corresponding third gear synchronizer 23, fourth gear synchronizer 24 and second gear synchronizer 22, third gear synchronizer can engage with third gear driven gear, and fourth gear synchronizer can engage with fourth gear driven gear, and second gear synchronizer can engage with second gear driven gear.Position corresponding on the second output shaft be then arranged with rotationally engage with three or five grades of driving gears five grades of driven gears 18, to keep off six grades of driven gears 19 that driving gear engages, the reverse gear driven gear 21 engaged with second gear driven gear, seven grades of driven gears 20 being meshed with seven grades of driving gears with four or six.In addition, second output shaft also needs arrange corresponding Five-gear synchronizer 25, six grades of synchronizers 26, reversing-gear synchronizer 28 and seven grades of synchronizers 27, Five-gear synchronizer can engage with five grades of driven gears, six grades of synchronizers can engage with six grades of driven gears, reversing-gear synchronizer can engage with reverse gear driven gear, and seven grades of synchronizers can engage with seven grades of driven gears.
In addition, we also need arrange the fourth gear driven gear synchronizer 29 that can engage with adjacent third gear driven gear on fourth gear driven gear, arrange six grades of driven gear synchronizers 30 that can engage with adjacent five grades of driven gears on six grades of driven gears simultaneously.
The present invention is provided with two driving gears respectively on the first input shaft and the second input shaft, and that is, only have four driving gears can complete the transmission of power of eight advance gears and a reverse gear in the axial direction, transfer route is as follows particularly for it:
When vehicle is with one grade of starting, gear switch is one grade, and self-clanging gear-shift engages with third gear driven gear by fourth gear driven gear synchronizer, and second gear synchronizer engages with second gear driven gear, the first automatic clutch now engages, and the second automatic clutch remains open state.The rotation of engine crankshaft passes to the first input shaft through the first automatic clutch, then the third gear driven gear on the first output shaft is passed to by grade driving gear of three or five on the first input shaft, because fourth gear driven gear synchronizer engages with third gear driven gear, therefore third gear driven gear drives fourth gear driven gear to rotate, and give four or six grades of driving gears on the second input shaft by transmission of power, then the second gear driven gear on the first output shaft is passed to by two reverse driving gears on the second input shaft, because second gear synchronizer engages with second gear driven gear, power can pass to the first output shaft by second gear driven gear, the gear ring of differential mechanism is passed to again by the first final gear rotated with the first output shaft synchronous, and through differential mechanism, transmission of power is gone out.
Work as vehicle acceleration, when reaching the shift point close to second gear, gear is changed to second gear by self-clanging gear-shift in advance, keep engaging with second gear driven gear by second gear synchronizer, fourth gear driven gear synchronizer is then thrown off with third gear driven gear, then unclamps the first automatic clutch, and engages the second automatic clutch, two clutches complete switching, and vehicle changes to second gear.The now rotation of bent axle passes to the second input shaft through the second automatic clutch, then the second gear driven gear on the first output shaft is passed to by two reverse driving gears on the second input shaft, because second gear synchronizer engages with second gear driven gear, power can pass to the first output shaft by second gear driven gear, passed to the gear ring of differential mechanism again by the first final gear rotated with the first output shaft synchronous, and through differential mechanism, transmission of power is gone out.
Work as vehicle acceleration, when needing to change to third gear by second gear, gear is changed to third gear by self-clanging gear-shift in advance, engage with third gear driven gear by third gear synchronizer, second gear synchronizer is then thrown off with second gear driven gear, then unclamps the second automatic clutch, and engages the first automatic clutch, two clutches complete switching, and vehicle changes to third gear.The now rotation of bent axle passes to the first input shaft through the first automatic clutch, then the third gear driven gear on the first output shaft is passed to by grade driving gear of three or five on the first input shaft, because third gear synchronizer engages with third gear driven gear, power can pass to the first output shaft by third gear driven gear, passed to the gear ring of differential mechanism again by the first final gear rotated with the first output shaft synchronous, and through differential mechanism, transmission of power is gone out.
Work as vehicle acceleration, when needing to change to fourth gear by third gear, gear is changed to fourth gear by self-clanging gear-shift in advance, engage with fourth gear driven gear by fourth gear synchronizer, third gear synchronizer is then thrown off with third gear driven gear, then unclamps the first automatic clutch, and engages the second automatic clutch, two clutches complete switching, and vehicle changes to fourth gear.The now rotation of bent axle passes to the second input shaft through the second automatic clutch, then the fourth gear driven gear on the first output shaft is passed to by grade driving gear of four or six on the second input shaft, because fourth gear synchronizer engages with fourth gear driven gear, power can pass to the first output shaft by fourth gear driven gear, passed to the gear ring of differential mechanism again by the first final gear rotated with the first output shaft synchronous, and through differential mechanism, transmission of power is gone out.
Work as vehicle acceleration, when needing to change to five grades by fourth gear, gear is changed to five grades by self-clanging gear-shift in advance, engage with five grades of driven gears by Five-gear synchronizer, fourth gear synchronizer is then thrown off with fourth gear driven gear, then unclamps the second automatic clutch, and engages the first automatic clutch, two clutches complete switching, and vehicle changes to five grades.The now rotation of bent axle passes to the first input shaft through the first automatic clutch, then five grades of driven gears on the second output shaft are passed to by grade driving gear of three or five on the first input shaft, because Five-gear synchronizer engages with five grades of driven gears, power can pass to the second output shaft by five grades of driven gears, passed to the gear ring of differential mechanism again by the second final gear rotated with the second output shaft synchronous, and through differential mechanism, transmission of power is gone out.
Work as vehicle acceleration, when needing to change to six grades by five grades, gear is changed to six grades by self-clanging gear-shift in advance, engage with six grades of driven gears by six grades of synchronizers, Five-gear synchronizer is then thrown off with five grades of driven gears, then unclamps the first automatic clutch, and engages the second automatic clutch, two clutches complete switching, and vehicle changes to six grades.The now rotation of bent axle passes to the second input shaft through the second automatic clutch, then six grades of driven gears on the second output shaft are passed to by grade driving gear of four or six on the second input shaft, because six grades of synchronizers engage with six grades of driven gears, power can pass to the second output shaft by six grades of driven gears, passed to the gear ring of differential mechanism again by the second final gear rotated with the second output shaft synchronous, and through differential mechanism, transmission of power is gone out.
Work as vehicle acceleration, when needing to change to seven grades by six grades, gear is changed to seven grades by self-clanging gear-shift in advance, engage with seven grades of driven gears by seven grades of synchronizers, six grades of synchronizers are then thrown off with six grades of driven gears, then unclamp the second automatic clutch, and engage the first automatic clutch, two clutches complete switching, and vehicle changes to seven grades.The now rotation of bent axle passes to the first input shaft through the first automatic clutch, then seven grades of driven gears on the second output shaft are passed to by grade driving gear of seven on the first input shaft, because seven grades of synchronizers engage with seven grades of driven gears, power can pass to the second output shaft by seven grades of driven gears, passed to the gear ring of differential mechanism again by the second final gear rotated with the second output shaft synchronous, and through differential mechanism, transmission of power is gone out.
Work as vehicle acceleration, when needing to change to eight grades by seven grades, gear is changed to eight grades by self-clanging gear-shift in advance, namely seven grades of synchronizers are kept to engage with seven grades of driven gears, and six grades of driven gear synchronizers are engaged with five grades of driven gears, then unclamp the first automatic clutch, and engage the second automatic clutch, two clutches complete switching, and vehicle changes to eight grades.The rotation of engine crankshaft passes to the second input shaft through the second automatic clutch, then six grades of driven gears on the second output shaft are passed to by grade driving gear of four or six on the second input shaft, because six grades of driven gear synchronizers engage with five grades of driven gears, therefore six grades of driven gears drive five grades of driven gears to rotate, and give three or five grades of driving gears on the first input shaft by transmission of power, then seven grades of driven gears on the second output shaft are passed to by grade driving gear of seven on the first input shaft, because seven grades of synchronizers engage with seven grades of driven gears, power can pass to the second output shaft by seven grades of driven gears, the gear ring of differential mechanism is passed to again by the second final gear rotated with the second output shaft synchronous, and through differential mechanism, transmission of power is gone out.
When we need reverse gear, reversing-gear synchronizer is engaged with reverse gear driven gear, then engage the second automatic clutch.The now rotation of engine crankshaft passes to the second input shaft through the second automatic clutch, then the second gear driven gear on the first output shaft is passed to by two reverse driving gears on the second input shaft, transmission of power is then given the reverse gear driven gear that the second output shaft engages with it by second gear driven gear, because reversing-gear synchronizer engages with reverse gear driven gear, power can pass to the second output shaft by reverse gear driven gear, passed to the gear ring of differential mechanism again by the second final gear rotated with the second output shaft synchronous, and through differential mechanism, transmission of power is gone out.
It should be noted that, because the second gear driven gear on the first output shaft needs to engage with the reverse gear driven gear on the second output shaft, therefore, first, second output shaft is not positioned at same plane with first, second coaxial input shaft, and three axis form triangular arrangement in space.In addition, be understandable that, should be separated from each other between two reverse driving gears in same plane and reverse gear driven gear.
Further, we also can be fixedly installed parking ratchet wheel 31 on the first output shaft.Because parking ratchet wheel much smaller than the moment of torsion of differential mechanism, therefore, will be arranged on the first output shaft by the moment of torsion of the first output shaft, be conducive to reducing parking braking power, thus reduce boundary dimension and the requirement of strength of halting mechanism.Because space is left in the position of seven grades of driving gears corresponding on the first output shaft, therefore, parking ratchet wheel preferably can be arranged on the position of the corresponding seven grades of driving gears of the first output shaft, thus makes parking ratchet wheel and seven grades of driving gears be positioned at same cross section.Certainly, parking ratchet wheel also can be fixedly installed on the second output shaft by we.
Claims (4)
1. a speed double-clutch formula automatic transmission, comprise differential mechanism, first input shaft, second input shaft the and optionally rotation of motor passed to the first automatic clutch of the first input shaft and optionally the rotation of engine crankshaft passed to the second automatic clutch of the second input shaft, second input shaft rotationally coaxial sleeve is connected on the first input shaft, first input shaft stretches out in the second input shaft away from engine crankshaft one end, first output shaft parallel with the second input shaft with the first input shaft and the second output shaft is provided with the second input shaft both sides at the first input shaft, first output shaft is installed with the first final gear engaged with the gear ring of differential mechanism, second output shaft is installed with the second final gear engaged with the gear ring of differential mechanism, it is characterized in that: the second half section stretching out in the second input shaft at the first input shaft is installed with three or five grades of driving gears near engine crankshaft one end, second input shaft keeps off driving gear and two reverse driving gears near three or five grades of driving gear one end to being installed with four or six successively near engine crankshaft one end, first output shaft is arranged with third gear driven gear rotationally that engage with three or five grades of driving gears, the fourth gear driven gear that driving gear engages is kept off with four or six, the second gear driven gear engaged with two reverse driving gears, first output shaft is also provided with corresponding third gear synchronizer, fourth gear synchronizer and second gear synchronizer, second output shaft is arranged with five grades of driven gears rotationally that engage with three or five grades of driving gears, six grades of driven gears that driving gear engages are kept off with four or six, the reverse gear driven gear engaged with second gear driven gear, second output shaft is also provided with corresponding Five-gear synchronizer, six grades of synchronizers and reversing-gear synchronizer, fourth gear driven gear is provided with the fourth gear driven gear synchronizer that can engage with third gear driven gear.
2. a kind of eight speed double-clutch formula automatic transmission according to claim 1, it is characterized in that, first input shaft is installed with seven grades of driving gears, second output shaft is then arranged with rotationally the seven grades of driven gears be meshed with seven grades of driving gears, the second output shaft is also provided with corresponding seven grades of synchronizers.
3. a kind of eight speed double-clutch formula automatic transmission according to claim 2, is characterized in that, six grades of driven gears are provided with six grades of driven gear synchronizers that can engage with five grades of driven gears.
4. the one eight speed double-clutch formula automatic transmission according to Claims 2 or 3, it is characterized in that, described first output shaft is installed with parking ratchet wheel, described parking ratchet wheel and seven grades of driving gears are positioned at same cross section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410363137.3A CN104373524B (en) | 2014-07-29 | A kind of eight speed double-clutch formula automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410363137.3A CN104373524B (en) | 2014-07-29 | A kind of eight speed double-clutch formula automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104373524A true CN104373524A (en) | 2015-02-25 |
| CN104373524B CN104373524B (en) | 2017-01-04 |
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| CN106523607A (en) * | 2015-09-14 | 2017-03-22 | 上海汽车集团股份有限公司 | Double-clutch automatic transmission and automobile |
| CN107035824A (en) * | 2017-06-06 | 2017-08-11 | 上海汽车变速器有限公司 | AMT automatic transmission assemblies |
| CN108016429A (en) * | 2016-10-31 | 2018-05-11 | 福特环球技术公司 | For engaging and departing from the method and system of vehicle stopped state |
| CN108105344A (en) * | 2017-12-20 | 2018-06-01 | 东风汽车集团有限公司 | A kind of compact seven keeps off double-clutch speed changer |
| CN108223703A (en) * | 2016-12-09 | 2018-06-29 | 辽宁丹东新弘源农业科技发展有限公司企业技术研究开发中心 | Vapour drags all-in-one machine combined type speed change transfer case |
| CN108397522A (en) * | 2018-04-25 | 2018-08-14 | 重庆青山工业有限责任公司 | The speed changer of oily electricity combination drive automobile |
| CN108412996A (en) * | 2018-04-25 | 2018-08-17 | 重庆青山工业有限责任公司 | Double drive new-energy automobile speed changer |
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| CN110578773A (en) * | 2018-06-08 | 2019-12-17 | 长城汽车股份有限公司 | eight-gear transmission |
| CN111853171A (en) * | 2019-04-25 | 2020-10-30 | 广州汽车集团股份有限公司 | Eight-speed double-clutch type automatic transmission and vehicle |
| CN112413061A (en) * | 2019-08-20 | 2021-02-26 | 广州汽车集团股份有限公司 | Six-speed automatic transmission and vehicle |
| CN113124110A (en) * | 2019-12-31 | 2021-07-16 | 上海汽车集团股份有限公司 | Double-clutch transmission and automobile |
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| CN115076306A (en) * | 2021-03-10 | 2022-09-20 | 广州汽车集团股份有限公司 | Nine-speed automatic transmission and vehicle |
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| CN106523607B (en) * | 2015-09-14 | 2019-01-04 | 上海汽车集团股份有限公司 | Double-clutch automatic gearbox and automobile |
| CN106523607A (en) * | 2015-09-14 | 2017-03-22 | 上海汽车集团股份有限公司 | Double-clutch automatic transmission and automobile |
| CN106321748A (en) * | 2016-10-11 | 2017-01-11 | 宁波上中下自动变速器有限公司 | Eight-speed double clutch speed change device |
| CN108016429A (en) * | 2016-10-31 | 2018-05-11 | 福特环球技术公司 | For engaging and departing from the method and system of vehicle stopped state |
| CN108016429B (en) * | 2016-10-31 | 2023-01-17 | 福特环球技术公司 | Method and system for engaging and disengaging a vehicle park condition |
| CN108223703A (en) * | 2016-12-09 | 2018-06-29 | 辽宁丹东新弘源农业科技发展有限公司企业技术研究开发中心 | Vapour drags all-in-one machine combined type speed change transfer case |
| CN108223703B (en) * | 2016-12-09 | 2023-09-12 | 周明和 | Combined type speed change transfer case for steam-driven integrated machine |
| CN107035824A (en) * | 2017-06-06 | 2017-08-11 | 上海汽车变速器有限公司 | AMT automatic transmission assemblies |
| CN107035824B (en) * | 2017-06-06 | 2023-07-28 | 上海汽车变速器有限公司 | AMT automatic transmission assembly |
| CN108105344A (en) * | 2017-12-20 | 2018-06-01 | 东风汽车集团有限公司 | A kind of compact seven keeps off double-clutch speed changer |
| CN108397522A (en) * | 2018-04-25 | 2018-08-14 | 重庆青山工业有限责任公司 | The speed changer of oily electricity combination drive automobile |
| CN108644339A (en) * | 2018-04-25 | 2018-10-12 | 重庆青山工业有限责任公司 | Hybrid vehicle multi-shifting speed variator |
| CN108412996A (en) * | 2018-04-25 | 2018-08-17 | 重庆青山工业有限责任公司 | Double drive new-energy automobile speed changer |
| CN108547918A (en) * | 2018-05-11 | 2018-09-18 | 浙江吉利控股集团有限公司 | Three fast dual clutch transmissions and electric vehicle |
| CN110578773A (en) * | 2018-06-08 | 2019-12-17 | 长城汽车股份有限公司 | eight-gear transmission |
| CN111853171A (en) * | 2019-04-25 | 2020-10-30 | 广州汽车集团股份有限公司 | Eight-speed double-clutch type automatic transmission and vehicle |
| CN112413061A (en) * | 2019-08-20 | 2021-02-26 | 广州汽车集团股份有限公司 | Six-speed automatic transmission and vehicle |
| CN112413061B (en) * | 2019-08-20 | 2024-04-19 | 广州汽车集团股份有限公司 | Six-speed automatic transmission and vehicle |
| CN113124110A (en) * | 2019-12-31 | 2021-07-16 | 上海汽车集团股份有限公司 | Double-clutch transmission and automobile |
| CN113492667A (en) * | 2020-03-20 | 2021-10-12 | 广州汽车集团股份有限公司 | Hybrid power driving system and vehicle |
| CN113915298A (en) * | 2020-07-08 | 2022-01-11 | 广州汽车集团股份有限公司 | Vehicle automatic gearbox and vehicle |
| CN114763822A (en) * | 2021-01-12 | 2022-07-19 | 广州汽车集团股份有限公司 | Nine-speed dual-clutch automatic transmission and vehicle |
| CN114763822B (en) * | 2021-01-12 | 2024-07-12 | 广州汽车集团股份有限公司 | Nine-speed double-clutch automatic transmission and vehicle |
| CN115076306A (en) * | 2021-03-10 | 2022-09-20 | 广州汽车集团股份有限公司 | Nine-speed automatic transmission and vehicle |
| CN115076306B (en) * | 2021-03-10 | 2024-06-07 | 广州汽车集团股份有限公司 | Nine-speed automatic transmission and vehicle |
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Effective date of registration: 20160122 Address after: 315336 Binhai New Area, Hangzhou Bay, Zhejiang, No. two, No. 818 Road, No. Applicant after: Ningbo lucky Luo You engine component Co., Ltd Applicant after: Zhejiang Geely Luoyou Engine Co., Ltd. Applicant after: Ji'nan Geely Auto Parts Co., Ltd. Applicant after: Hunan Luoyou Engine Parts Co., Ltd. Applicant after: Ningbo Shangzhongxia Automatic Transmission Co., Ltd. Applicant after: Zhejiang Geely Holding Group Co., Ltd. Address before: 315336 Binhai New Area, Hangzhou Bay, Zhejiang, No. two, No. 818 Road, No. Applicant before: Ningbo lucky Luo You engine component Co., Ltd Applicant before: Zhejiang Geely Luoyou Engine Co., Ltd. Applicant before: Ji'nan Geely Auto Parts Co., Ltd. Applicant before: Hunan Luoyou Engine Parts Co., Ltd. Applicant before: Shandong Jili Transmission Co., Ltd. Applicant before: Ningbo Shangzhongxia Automatic Transmission Co., Ltd. Applicant before: Hunan Jisheng International Power Transmission System Co., Ltd. Applicant before: Zhejiang Geely Holding Group Co., Ltd. |
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