CN102128237A - Dual clutch multi-speed transmission and vehicle having a dual clutch multi-speed transmission - Google Patents
Dual clutch multi-speed transmission and vehicle having a dual clutch multi-speed transmission Download PDFInfo
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- CN102128237A CN102128237A CN2011100045329A CN201110004532A CN102128237A CN 102128237 A CN102128237 A CN 102128237A CN 2011100045329 A CN2011100045329 A CN 2011100045329A CN 201110004532 A CN201110004532 A CN 201110004532A CN 102128237 A CN102128237 A CN 102128237A
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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
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—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
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
- F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
- F16H61/688—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
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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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds
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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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
Abstract
A dual clutch multi-speed transmission 1 comprises a first input shaft 2 engageable by a first drive clutch 4, a second input shaft 3 engageable by a second drive clutch 5. A single output shaft 7, an intermediate shaft 6 and a first torque transmitting path for driveably coupling the intermediate shaft 6 to the output shaft 7 are also provided. The first torque transmitting mechanism comprises a first gear set 11 having a first gear 12 intermeshing with a second gear 13 and with a third gear 14. The first gear 12 is mounted on the first input shaft 2 or the second input shaft 3, the second gear 13 is mounted on the intermediate shaft 6 and the third gear 14 is mounted on the output shaft 7. Preferably the fist gear 12 is rotatable about the first 2 or second 3 input shafts while the second 13 and third 14 gears are fixed for common rotation with the intermediate 6 and output 7 shafts. The invention also relates to a vechile having the transmission.
Description
Technical field
The present invention relates to two clutch multi-speed transmissions and vehicle with two clutch multi-speed transmissions.
Background technique
Speed changer is used for initial actuator (such as motor) is connected to last actuator (such as differential mechanism) with the velocity ratio of certain limit.For example, the speed changer of Motor Vehicle can than between provide at five and eight forward velocity ratio and at least one reverse gear.
Transmission of power from initial actuator to speed changer usually each gear than before changing or during be interrupted because be not actuated when the transferring power such as the such torque transmitter of synchronizer.
Such as at US 7,353, the double-clutch speed changer that discloses among the 724B2 can be operating as transferring power from odd gear to even number gear change process.The double-clutch speed changer shell thinks to have two automaitc shfit manual transmissions, and one provide odd gear, and one provides the even number gear.Each speed changer is connected to motor by independent engine clutch, thereby the gear shift between odd gear and the even number gear can realize and not having the interruption of kinetic current.
For example, when odd gear was moved, synchronizer was actuated to making speed changer be used for next even number gear.Actuate to making before odd gear disconnects from motor at the engine clutch of odd gear, the engine clutch of even number gear can be actuated to motor being attached to the even number gear.Therefore, in double-clutch speed changer with gear than when the odd number shelves change to the even number shelves, continuous kinetic current can be provided.
But also expectation provides a kind of speed changer, and it is compact and lighter, so that can hold speed changer in vehicle, and does not gain in weight, and gaining in weight causes reducing the fuel efficiency of vehicle.Particularly, in so-called miniature, mini and compact car, the space that can be used for speed changer is limited especially, thereby for these automobiles, compact speed changer needs.
Therefore, expectation provides efficiently and also compact multi-speed transmission.
Summary of the invention
The application provides a kind of pair of clutch multi-speed transmission, it comprises can be by first input shaft of the first driving clutch, can be by second input shaft of the second driving clutch, single output shaft, jack shaft and first torque transmission paths that is used for jack shaft can be attached to drivingly output shaft.First torque transmission paths comprises first gear train, and it has with second gear and intermeshes and intermeshing first gear of the 3rd gear.First gear is installed on first input shaft or second input shaft, and second gear is installed on the jack shaft, and the 3rd gear is installed on the output shaft.
First gear is positioned between second gear and the 3rd gear, so that the two intermeshes with second gear and the 3rd gear.First gear train can be coplanar.
First torque transmission paths provides a path, and by this path, moment of torsion can be delivered to output shaft via first input shaft from jack shaft, thereby jack shaft can drive output shaft.This layout makes speed changer encapsulate more compactly, is used for using in miniature, mini and/or compact car.This layout also makes speed changer have single output shaft because moment of torsion from jack shaft via being installed in gear transmission on first or second input shaft to this single output shaft.Single output shaft makes speed changer be set in the compact packing, and also simplifies the control of speed changer.
Being installed in gear on the axle can be connected for around this rotation or be mounted for around the common rotation of this axle.
The gear that is connected for rotating also can be described to the gear of pine, and it can be connected to its corresponding axle by torque-transmitting mechanisms (such as clutch or synchronizer).When gear is connected to its axle by optionally actuating clutch, this gear and the common rotation of its axle, and can drive this axle, or by this axle driving.
The gear that is connected for the common rotation of its corresponding axle also can be described as fixing gear.
The gear of gear train also can be described as gearwheel, and comprises a plurality of teeth, described tooth from its circumference outstanding and with the tooth engagement of the second and the in certain embodiments the 3rd gear or gearwheel.
First input shaft and second input shaft can be provided with one heart.First input shaft can provide by interior bar, and second input shaft can provide by the hollow stem around first input shaft.Single output shaft can be connected to final driver element or differential mechanism.
Output shaft can radially be shifted from first and second input shafts.Jack shaft can radially be shifted from two input shafts and single output shaft.
In one embodiment, first gear can be connected for around first input shaft or the rotation of second input shaft, and second gear can be connected for rotating jointly around jack shaft, and the 3rd gear can be connected for rotating jointly around output shaft.
In this embodiment, the central gear of first gear train is loose, and two external gears of gear train are fixed.Therefore, moment of torsion can from the second fixing gear, via first gear transmission of pine to the 3rd fixing gear, so that moment of torsion is delivered to output gear and drives output shaft from jack shaft.
In other embodiments, two clutch multi-speed transmissions comprise that also second torque transmission paths is used for first input shaft or second input shaft can be connected to jack shaft drivingly.Second torque transmission paths comprises and first gear train at interval second gear train axially.
Second gear train comprises the 4th gear and the 5th gear, and the 4th gear is connected for rotating jointly around first input shaft or second input shaft, and the 5th gear is connected for rotating around jack shaft.The 4th gear is fixed on first input shaft or on second input shaft, the 5th gear is loose on jack shaft.Second torque transmission paths also comprises first torque-transmitting mechanisms, and it selectively engages so that the 5th gear is connected to jack shaft, is used to make the 5th gear and jack shaft to rotate jointly.
Second torque transmission paths and first torque transmission paths provide when using from first input shaft or second input shaft via the torque transmission paths of jack shaft to output shaft, to drive output shaft together.
For this torque transmission paths is provided, first transfer mechanism is selectively engaged so that the 5th gear is connected to jack shaft.Moment of torsion from initial actuator is delivered to the 4th gear via first input shaft or second input shaft, the 5th gear from the 4th gear transmission to second gear train, from the 5th gear transmission to jack shaft, from jack shaft to second gear, via three gear of first gear transmission to first gear train, then from the 3rd gear to output shaft, and finally arrive last actuator or differential mechanism.
In another embodiment, two clutch multi-speed transmissions also comprise second torque-transmitting mechanisms, and it selectively engages first gear is connected to first input shaft or second input shaft, are used for correspondingly rotating jointly with first input shaft or second input shaft.When second torque-transmitting mechanisms was selectively engaged, moment of torsion flow to output shaft from first input shaft or second input shaft via first gear and the 3rd gear.In this embodiment, first torque-transmitting mechanisms not with jack shaft on the 5th gear engagement, thereby first gear and the 3rd gear use second gear and jack shaft as idle pulley, and first gear and the 3rd gear and first gear train drive output shaft.
Therefore, first gear train has dual purpose.In a purposes, first gear train is used to provide first torque transmission paths, so that jack shaft can be connected to output shaft drivingly.In second purposes, first gear train is used to by the first and the 3rd gear of first gear train first or second input shaft can be connected to output shaft drivingly.The feasible close package that can be provided for speed changer of this dual purpose of first gear train.
In another embodiment, be arranged on the jack shaft the 5th gear be connected for intermeshing around the reverse gear that output shaft rotates.The 3rd torque-transmitting mechanisms is arranged on the output shaft, and it optionally engages so that reverse gear is connected to output shaft.When the 3rd torque-transmitting mechanisms is connected to output shaft with reverse gear, moment of torsion from first input shaft or second input shaft via the 4th gear, the 5th gear transmission to the reverse gear of the common rotation of output shaft, the 4th gear is fixed on first input shaft or second input shaft, and the 5th gear dallies on jack shaft.
Second gear train can provide two different torque transmission paths.In one embodiment, second gear train can be used to moment of torsion is delivered to jack shaft with the velocity ratio of advancing from first input shaft or second input shaft, so that the reverse speed ratio to be provided.In one embodiment, second gear train can be used for not providing speed to be delivered to jack shaft than ground from first input shaft or second input shaft moment of torsion, so that the reverse speed ratio to be provided.
Jack shaft can be used to realize a velocity ratio or a plurality of velocity ratio by one or more local gear trains are installed on jack shaft.Local gear train can be with first input shaft or second input shaft on the intermeshing single gear of second gear.
In another embodiment, two clutch multi-speed transmissions also comprise the 3rd gear train, and itself and first gear train and second gear train are axially at interval.The 3rd gear train comprises the 7th gear that is connected for common the 6th gear that rotates of first input shaft and is connected for rotating around jack shaft.The 6th gear is fixed on the input shaft thus, and the 7th gear is loose on jack shaft.The 4th gear that this embodiment can be used for second gear train also is fixed on the embodiment on first input shaft.
First torque-transmitting mechanisms can be two torque-transmitting mechanisms, and optionally engages, and is connected to jack shaft with the 5th gear with second gear train, or the 7th gear of the 3rd gear train is connected to jack shaft.In these embodiments, wherein, jack shaft is used to provide two or more velocity ratios, and first gear train can be used to moment of torsion is delivered to output shaft from jack shaft via first or second input shaft, to drive output shaft, as mentioned above.
In this embodiment, two clutch multi-speed transmissions comprise three double-direction twist moment transfer mechanisms.A double-direction twist moment transfer mechanism is connected to jack shaft, and a double-direction twist moment transfer mechanism is connected to second input shaft, and a double-direction twist moment transfer mechanism is connected to output shaft.This embodiment can be used for providing five forward velocity ratios and a reverse speed ratio, and wherein, the reverse speed ratio is synchronized.The double-direction twist moment transfer mechanism can provide by two synchronizers.
In another embodiment, first gear of first gear train is connected for around the rotation of first input shaft, and the 4th gear of second gear train is connected for rotating jointly with second input shaft.First gear is loose on first input shaft thus, and the 4th gear is fixed on second input shaft.In this embodiment, first be positioned in the foregoing description with the 4th gear and compare on the different input shafts.
But in other embodiments, first gear of first gear train and the 4th gear of second gear train can be set on the same input shaft.In one embodiment, first gear is connected for around the rotation of second input shaft, and the 4th gear is connected for rotating jointly with second input shaft.In this embodiment, first gear is loose on second input shaft, and the 4th gear is fixed on second input shaft.
Be connected for rotating among the embodiment of (promptly fixed thereon) with second input shaft at the 4th gear, two clutch multi-speed transmissions can comprise two unidirectional torque transfer mechanisms and two double-direction twist moment transfer mechanisms.A unidirectional torque transfer mechanism is coupled to jack shaft and first torque-transmitting mechanisms is provided, and it optionally engages so that the 5th gear is connected to jack shaft.In these embodiments, second gear train can be used for only moment of torsion being delivered to jack shaft from second input shaft, and the forward velocity ratio of speed changer is not provided itself.
One of the double-direction twist moment transfer mechanism can be connected to input shaft, and another double-direction twist moment transfer mechanism and remaining unidirectional torque transfer mechanism can be connected to output shaft.Alternatively, two double-direction twist moment transfer mechanisms can be connected to output shaft, and remaining unidirectional torque transfer mechanism can be connected to first input shaft.
These layouts of torque-transmitting mechanisms can be used for providing the two clutch multi-speed transmissions with five forward velocity ratios and a reverse speed ratio, and wherein, not only forward velocity ratio but also reverse speed are than all being synchronized.
The application also provides a kind of power train, comprises initial actuator, any described pair of clutch multi-speed transmission and last actuator or differential mechanism among the embodiment as described above.
The application also provides a kind of vehicle, comprises as described above any described pair of clutch multi-speed transmission among the embodiment.
Description of drawings
With reference to accompanying drawing embodiment is described.
Fig. 1 a to 1g shows the two clutch multi-speed transmissions according to first embodiment, wherein
Fig. 1 a shows the torque-flow that is used for first forward velocity ratio by speed changer;
Fig. 1 b shows the torque-flow that is used for second forward velocity ratio by speed changer;
Fig. 1 c shows the torque-flow that is used for the 3rd forward velocity ratio by speed changer;
Fig. 1 d shows the torque-flow that is used for the 4th forward velocity ratio by speed changer;
Fig. 1 e shows the torque-flow that is used for the 5th forward velocity ratio by speed changer;
Fig. 1 f shows the torque-flow that is used for the reverse speed ratio by speed changer;
Fig. 1 g shows gear that first embodiment's speed changer provides than (gear ratio);
Fig. 2 a to 2f shows the two clutch multi-speed transmissions according to second embodiment, wherein
Fig. 2 a shows the torque-flow that is used for first forward velocity ratio by speed changer;
Fig. 2 b shows the torque-flow that is used for second forward velocity ratio by speed changer;
Fig. 2 c shows the torque-flow that is used for the 3rd forward velocity ratio by speed changer;
Fig. 2 d shows the torque-flow that is used for the 4th forward velocity ratio by speed changer;
Fig. 2 e shows the torque-flow that is used for the 5th forward velocity ratio by speed changer;
Fig. 2 f shows the torque-flow that is used for the reverse speed ratio by speed changer;
Fig. 3 a to 3f shows the two clutch multi-speed transmissions according to the 3rd embodiment, wherein
Fig. 3 a shows the torque-flow that is used for first forward velocity ratio by speed changer;
Fig. 3 b shows the torque-flow that is used for second forward velocity ratio by speed changer;
Fig. 3 c shows the torque-flow that is used for the 3rd forward velocity ratio by speed changer;
Fig. 3 d shows the torque-flow that is used for the 4th forward velocity ratio by speed changer;
Fig. 3 e shows the torque-flow that is used for the 5th forward velocity ratio by speed changer;
Fig. 3 f shows the torque-flow that is used for the reverse speed ratio by speed changer;
Fig. 4 a to 4f shows the two clutch multi-speed transmissions according to the 4th embodiment, wherein
Fig. 4 a shows the torque-flow that is used for first forward velocity ratio by speed changer;
Fig. 4 b shows the torque-flow that is used for second forward velocity ratio by speed changer;
Fig. 4 c shows the torque-flow that is used for the 3rd forward velocity ratio by speed changer;
Fig. 4 d shows the torque-flow that is used for the 4th forward velocity ratio by speed changer;
Fig. 4 e shows the torque-flow that is used for the 5th forward velocity ratio by speed changer;
Fig. 4 f shows the torque-flow that is used for the reverse speed ratio by speed changer;
Fig. 5 shows the gear ratio that embodiment 2 to 4 speed changer provides.
Description of reference numerals
1; 1 '; 1 "; 1 " ' speed changer
2 first input shafts
3 second input shafts
4 first drive clutch
5 second drive clutch
6 jack shafts
7 output shafts
8 output pinions
9 ring gears
10 differential mechanisms
11 first gear trains
12 first gears
13 second gears
14 the 3rd gears
15 second gear trains
16 the 4th gears
17 the 5th gears
18 the 3rd gear trains
19 the 6th gears
20 the 7th gears
21 the 4th gear trains
22 octadentates wheel
23 the 9th gears
24 the 5th gear trains
25 the tenth gears
26 the 11 gears
27 reverse gears
28 first bi-directional synchronization devices
29 second bi-directional synchronization devices
30 the 3rd bi-directional synchronization devices
31 first one-way synchronization devices
32 second one-way synchronization devices
33 first bi-directional synchronization devices
34 second bi-directional synchronization devices
Embodiment
Fig. 1 a to 1f shows the two clutch multi-speed transmissions 1 according to first embodiment.
Two clutch multi-speed transmissions 1 according to first embodiment comprise first input shaft 2 and second input shaft 3 that is provided with around this first input shaft 2 with one heart.First input shaft 2 provides by solid hopkinson bar, and second input shaft 3 provides by hollow stem.First input shaft 2 can be driven clutch 4 by first and engage.Second input shaft 3 can be driven clutch 5 by second and engage.
Each all comprises band tooth gearwheel (toothed gear wheel) gear of the different gear trains in the double-clutch speed changer among all embodiments.
The 4th forward velocity provides than first gear 12 and the 3rd gear 14 by first gear train.Therefore, first gear train 11 has dual purpose, and provide the 4th forward gear than and from jack shaft 6 to output shaft 7 torque transmission paths.
When the axis of input shaft 2,3, jack shaft 6 and output shaft 7 is observed, these have the layout of general triangular, and wherein, jack shaft 6 is positioned at the place, summit on first and second input shafts 2,3 and the output shaft 7.Output shaft 7 is laterally orientated as near two input shafts 2,3 with one heart.
The second pair of synchronizer 29 is connected to second input shaft 3 between the 6th gear 19 of first gear 12 of first gear train 11 and the 3rd gear train 18, so that first gear 12 or the 6th gear 19 can be connected to second input shaft 3, be used for rotating jointly with second input shaft 3.When being connected to, first gear 12 is used for rotating jointly with second input shaft 3, first gear train 11 and especially, and first gear 12 and the 3rd gear 14 of first gear train 11 can drive output shaft 7.When the 6th gear 19 was connected for the 3 common rotations of second input shaft, the 3rd gear train 18 can drive output shaft 7.
The 3rd pair of synchronizer 30 is connected to output shaft 7 and is positioned between the 11 gear 26 and reverse gear 27 of the 5th gear train 24, be used for rotating jointly so that connect reverse gear 27 or the 11 gear 26, thereby reverse gear or the 5th reverse gearset can drive output shaft 7 with output shaft 7.
The diameter of each gear and jack shaft 6 and last axle 7 are also shown in the drawings apart from the displacement of the common axis of first input shaft 2 and second input shaft 3.
Odd number forward velocity ratio, that is, the first, the 3rd and the 5th forward gears provides by second gear train 15, the 4th gear train 21 and the 5th gear train 24 respectively.These gear trains are represented with numeral 1,3 and 5 in the accompanying drawings.Provide the gear train 15,21 and 25 of odd number forward velocity ratio to be connected to first input shaft 2.Even number forward velocity ratio, that is, the second and the 4th forward gears is provided by first gear train 11 and the 3rd gear train 18, and is coupled to second output shaft 3.These gear trains are represented with numeral 2 and 4 in the accompanying drawings.Reverse speed gear 27 is represented with R in the accompanying drawings.
First input shaft, 2 to the second input shafts 3 are long, and outstanding above second input shaft 3, thereby provide the gear train 15,21 and 24 of odd number shelves to orientate as near the gear train 11,18 that the even number gear is provided.
Fig. 1 a shows the torque-flow that is used for first forward velocity ratio by speed changer.First drives clutch 4 is actuated to engage and to drive first input shaft, 2, the first synchronizers 28 and is optionally actuated with the 5th gear 17 that engages second gear train and connect it and be used for rotating jointly with jack shaft 6.
Moment of torsion is delivered to jack shaft 6 from initial actuator by the 4th gear 16 and the 5th gear 17 of first input shaft 2 by second gear train 15.Moment of torsion is delivered to three gear 14 that be fixed on output shaft 7 on from jack shaft 6 via the second fixing gear 13 on the jack shaft 6, first gear 12 of pine on second input shaft 3 by first gear train 11 then, so that drive output shaft 7.Moment of torsion transmits from output shaft 7 then, to drive differential mechanism by output pinion 8 and ring gear 9.Torque path has the pitch of the laps path, and it has clockwise circular annulus.
In order to compare second forward velocity than gear shift from first forward velocity, second synchronizer 29 optionally engages with the 6th gear 19 of the 3rd gear train 18, so that the 6th gear 19 is connected to second input shaft 3, is used for rotating jointly with second input shaft 3.First drives clutch 4 disconnects from first input shaft 2, so that first input clutch 4 is disconnected from initial actuator, second drives clutch 5 approximately engages with second input shaft 3 simultaneously.Thus, one grade the torque-flow of being used for as shown in Figure 1a interrupts between the initial actuator and first input shaft 2.
The torque-flow that is used for second forward velocity ratio by speed changer 1 is shown in Fig. 1 b.Moment of torsion flows from initial actuator, and directly is delivered to output shaft 7 via the 6th gear 19 and the 7th gear 20 of second input shaft 3 by the 3rd gear train 18, to drive output shaft and differential mechanisms 10 by output pinion 8 and ring gear 9.
For from second forward velocity than gear shift to the three forward velocity ratio, the 9th gear 23, second engine clutch 5 that first synchronizer 28 is connected to the 4th gear train 21 disconnect from second input shaft 3, first engine clutch 4 engages with first input shaft 2.First input shaft 2 is driven by initial actuator now.
Fig. 1 C show when select the 3rd forward velocity than the time the torque-flow that passes through speed changer 1.Moment of torsion is delivered to speed changer 1 from initial actuator via first input shaft 2, and octadentate wheel the 22 and the 9th gear 23 via the 4th gear train 21 is passed to jack shaft 6 then.Moment of torsion is delivered to output shaft 7 by first torque-transmitting mechanisms of first gear train 11 from jack shaft 6.
Especially, moment of torsion is by being connected for being delivered to second gears 13 of the common rotation of jack shaft 6 first gear 12 of idle running on second input shaft 2, then to being connected for the 4th gears 14 with output shaft 7 common rotations with driving output shaft 7.Moment of torsion is delivered to differential mechanism by output pinion 8 and ring gear 9 from output shaft 7 then.
For from the 3rd forward velocity than gear shift to the four forward velocity ratio, second synchronizer 29 is connected to first gear 12 and is used for rotating jointly with second output shaft 3.The second initial clutch 5 engages with second input shaft 3, and the first initial clutch 5 disconnects from first input shaft 2.Torque-flow to first input shaft 2 is interrupted, and second input shaft 3 is existing by initial actuator driving.
Shown in Fig. 1 d, moment of torsion flow to second input shaft 3 from initial actuator, and drives output shaft 7 via first gear 12 and the 3rd gear 14 of first gear train 11.Moment of torsion flow to differential mechanism 10 by output pinion 8 and ring gear 9 from output shaft 7.
Therefore, first gear train 11 provides first torque path, be used for moment of torsion is delivered to output shaft 7 from jack shaft 6, thereby when first gear 12 was connected for the 3 common rotations of second input shaft, the second and the 4th gear train 15,21 that is arranged on the jack shaft 6 can drive output shaft 7 and the 4th forward velocity ratio and drive output shaft by moment of torsion is delivered to output shaft 7 from second input shaft 3.First synchronizer 28 is not connected to the 9th gear 23 or the 5th gear 17 that is connected for around jack shaft 6 rotations.When the 4th forward velocity when selected, be fixed on the 3rd gear 13 and jack shaft 6 idle running of first gear train 11 on the jack shaft 6.
For from the 4th forward velocity gear shift to the five forward velocity, the 3rd synchronizer 30 optionally engages with the 11 gear 26 of the 5th gear train 24, first drives clutch 4 is engaged to first input shaft 2, second drives clutch 5 disconnects from second input shaft 3, thereby moment of torsion is delivered to first input shaft 2 from initial actuator.
Fig. 1 e shows when the torque-flow of the 5th forward velocity when selected.When the 5th forward velocity when selected, moment of torsion is directly delivered to output shaft 7 via the tenth gear 25 and the 11 gear 26 of the 5th gear train 24 from first input shaft 2, to drive output shaft 7.
Be used to provide the torque-flow of reverse gear ratio shown in Fig. 1 f.First engine clutch 4 engages with first input shaft 2, and second drives clutch 5 disconnects from second input shaft 3, is used for the reverse speed ratio.The 3rd synchronizer 30 engages with reverse gear 27, is used for common rotation so that reverse gear 27 is connected with output shaft 7.The 5th gear 17 that is connected for rotation on jack shaft 6 of the reverse gear 27 and second gear train 15 intermeshes.For the reverse speed ratio is provided, first synchronizer 28 is not attached to the 5th gear 17, thus the idle running of the 5th gear.Moment of torsion is delivered to the 4th gear 16 and the 5th gear 17 of second gear train 15 by first input shaft 2 from initial actuator, is delivered to the reverse gear 27 that is connected to output shaft 7 from the 5th gear 17 in jack shaft 6 idle running, to drive output shaft 7.
The forward velocity ratio of speed changer 1 and the obtainable gear ratio of each of reverse speed ratio are shown in Fig. 1 g.Target ratio is compulsory, and the predetermined desired ratio of expression.
Fig. 2 a to 2f shows the speed changer 1 ' according to second embodiment.Second embodiment's speed changer 1 ' comprises first input shaft 2 and second input shaft 3, jack shaft 6 and single output shaft 7 of concentric setting as first embodiment.
Also, provide the gear train of odd number forward velocity ratio to be driven, provide the gear train of even number forward velocity ratio to be driven by second input shaft 3 by first input shaft 2 as first embodiment.But anti-with first embodiment, the reverse speed ratio is driven by second input shaft 3, rather than first input shaft 2.
Second embodiment's speed changer 1 ' also is with first embodiment's the different of speed changer, the axial position of gear train, the quantity of the torque-transmitting mechanisms that is provided and position.
The gear train of second embodiment's speed changer 1 ' is in the following order from being input to first and second input shafts, 2,3 beginnings setting axially spaced apart from each other: second gear train 15, the 3rd gear train 18, first gear train 11, the 4th gear train 21 and the 5th gear train 24.Reverse gear 27 and second gear train, 15 coplanars, and be positioned at the end opposite (comparing) of output shaft 7 with the first embodiment position shown in Fig. 1 a to 1f.
In second embodiment's speed changer 1 ', moment of torsion transmits in opposite direction, and it transmits by jack shaft 6 in the accompanying drawings from right to left, compares with first embodiment's speed changer 1, and wherein, moment of torsion transmits by jack shaft 6 in the accompanying drawings from left to right.
Speed changer 1 ' also comprises the 3rd gear train 18, and it comprises that the 6th gear 19, the six gears 19 that are mounted for around the 3 common rotations of second input shaft are meshing with each other with the 7th gear that is connected to around output shaft 7 rotations.
Speed changer 1 ' comprises the 4th gear train 21, and it comprises and the 9th gear 23 intermeshing octadentate wheels 22.Octadentate wheel 22 is connected for around 2 rotations of first input shaft.Opposite with first embodiment, the 9th gear is connected for rotating jointly around output shaft 7, rather than around jack shaft 6.
The 5th gear train 24 comprises and the 11 gear 26 intermeshing the tenth gears 25.As first embodiment, the tenth gear 25 is mounted for rotating jointly around first input shaft 2, and the 11 gear 26 is mounted for around output shaft 7 rotations.
Speed changer 1 ' according to second embodiment comprises four synchronizers.Two of four synchronizers is the one-way synchronization device, and two of four synchronizers are two or the bi-directional synchronization device.The first one-way synchronization device 31 is connected to jack shaft 7, so that optionally engage with the 5th gear 17 of second gear train 15.
One of double clutch 33 is installed in second input shaft 2, so that optionally engage with first gear 12 of first gear train 11 or the octadentate wheel 22 of the 4th gear train 21.Two synchronizers are connected to output shaft 7.One-way synchronization device 32 is connected to output shaft 7, so that optionally engage with the 11 gear 26 of the 5th gear train 24.Two synchronizers 34 are connected to output shaft 7, so that optionally engage with the 6th gear 19 or the reverse gear 17 of the 3rd gear train 18.
The 5th gear 17 of the reverse gear 27 and second gear train 15 intermeshes, and with second gear train, 15 coplanars.The 4th gear 16 of the reverse gear 27 and second gear train 15 at interval.
In second embodiment's speed changer 1 ', first forward velocity provides than by first gear train 24, second speed ratio and the 5th forward velocity provide than by first gear train 11, the 3rd forward velocity provides than by the 4th gear train 21, the 4th forward velocity provides than by the 3rd gear train 18, and second gear train 15 is used to provide the reverse speed ratio.
Fig. 2 a to 2f show five forward velocity that speed changer 1 ' provides than and the torque-flow of a reverse speed ratio, it is delivered to last actuator (shown in the drawings is differential mechanism 10) with moment of torsion from unshowned initial actuator (such as internal-combustion engine).
For with speed changer 1 ' gear shift to first forward velocity ratio, first drives clutch 4 engages with first input shaft 2, the second driving clutch 5 is from 3 disconnections of second input shaft.First input shaft 2 drives by initial actuator, and the torque-flow from initial actuator to second input shaft 3 is interrupted.The 3rd synchronizer 32 engages with the 11 gear 26 of the 5th gear train 24.Moment of torsion is delivered to output shaft 7 by first input shaft 2 via the tenth gear the 25, the 11 gear 26, to drive output shaft, single output pinion 8, ring gear 9 and differential mechanism 10.
For with the first forward velocity gear shift to second forward velocity, first synchronizer 31 optionally engages with the 5th gear 17, is used for rotating jointly with jack shaft 6 so that connect the 5th gear 17.First drives clutch 4 disconnects from first input shaft 2, and second drives clutch 5 engages with second input shaft 3.
Fig. 2 b show when select second forward velocity than the time torque-flow.Moment of torsion transmits by four gear 16 and five gear 17 of second input shaft 3 via second gear train 15 from initial actuator, to drive the jack shaft 6 and first gear train 11, so that drive output shaft 7, output pinion 8, ring gear 9 and differential mechanism 10, this first gear train 11 comprises second gear 13 that is fixed on the jack shaft 6, around first gear 12 of first input shaft, 2 idle running be fixed on the 3rd gear 14 on the output shaft 7.Second gear train 15 is used to that moment of torsion is delivered to jack shaft 6, the first gear trains from second input shaft 3 and is used to via first gear 11 of idle running on first input shaft 2 moment of torsion is delivered to output shaft 7 from jack shaft 6.
For from the second forward velocity gear shift to the, three forward velocity, second synchronizer 33 optionally engages with the octadentate wheel 22 of the 4th gear train 21, and second drives clutch 5 disconnects from second input shaft 3, and the first driving clutch 4 engages with first input shaft 2.
In case select the 3rd forward velocity, shown in Fig. 2 c, moment of torsion is delivered to output shaft 7 from initial actuator by octadentate wheel the 22, the 9th gear 23 via first input shaft 2, the 4th gear train 21, and is passed to differential mechanism 10 by output pinion 8 and ring gear 9.
For from the 3rd forward velocity than gear shift to the four forward velocity ratio, the 4th synchronizer 34 optionally engages with the 7th gear 24, is used for rotating jointly with output shaft 7 to connect the 7th gear 24.First drives clutch 4 disconnects from first input shaft 2, and second drives clutch 5 engages with second input shaft 3.
When the 4th forward velocity torque-flow by speed changer 1 ' when selected shows in Fig. 2 d.Be delivered to the 6th gear 19 and the 7th gear 20 of the 3rd gear train 18 from the moment of torsion of initial actuator by second input shaft 3, to drive output shaft 7 and differential mechanisms 10 via output pinion 8 and ring gear 9.
For from the 4th forward velocity than gear shift to the five forward velocity ratio, second synchronizer 33 optionally engages with first gear 12 of first gear train 11, second drives clutch 5 disconnects from second input shaft 3, first drives clutch 4 engages with first input shaft 2.
When selecting the 5th forward velocity, moment of torsion is delivered to first gear 12 and the 3rd gear 14 of first gear train 11 from initial actuator by input shaft 2, to drive output shaft 7, output pinion 8, ring gear 9 and differential mechanism 10 shown in Fig. 2 e.Because first gear 12 also intermeshes with second gear 13 that is connected for jack shaft 6 common rotations, second gear 13 and jack shaft 6 dally when the 5th forward velocity is selected.
Reverse speed than by with double clutch 34 optionally engaged reverse gear 27 be provided, thereby reverse gear 27 rotates jointly with output shaft 7.The second driving clutch 5 and second input shaft 3 rotate jointly, and first drives clutch 4 disconnects from first input shaft 2.Moment of torsion is delivered to the reverse gear 27 that be arranged on output shaft 7 on by second input shaft 3 via the 5th gear 17 of fixing the 4th gear 16 and pine of second gear train 15 from initial actuator, thereby reverse gear 27 drives output shaft 7, because reverse gear 27 and the 5th gear 17 intermesh.
The torque-flow that is used for the reverse speed ratio is shown in Fig. 2 f.In case select the reverse speed ratio, be mounted for driving reverse gear 27 via the 5th gear 17 around jack shaft 6 idle running around the 4th gear 16 of second input shaft, 3 common rotations, this reverse gear optionally is connected to output shaft 7, is used for rotating jointly with output shaft 7.
Fig. 3 a to 3f shows the speed changer 1 according to the 3rd embodiment ".In the 3rd embodiment, speed changer 1 " the gear train order identical with second embodiment with gear around the layout of jack shaft 2, second input shaft 3 and output shaft 7.The 3rd embodiment and second embodiment's difference are the wherein layout of two synchronizers.
Compare with second embodiment's speed changer 1 ', at the 3rd embodiment's speed changer 1 " in, the octadentate wheel 22 of the 4th gear train 21 is connected for rotating jointly with first input shaft 2, and the 9th gear 23 is mounted for and output shaft 7 rotations.
As first and second embodiments, the odd number forward velocity is than being driven by first input shaft 2, and the even number forward velocity is than being driven by second input shaft 3.Reverse gear 27 is driven by second input shaft 3, as second embodiment.
For with speed changer 1 " gear shift is to first forward velocity ratio, and first drives clutch 4 engages with first input shaft, and the second driving clutch 5 is from 3 disconnections of second input shaft.Two synchronizers 33 engage with the 11 gear 26 of the 5th gear train 24.Shown in Fig. 3 a, moment of torsion is delivered to output shaft 7 by first input shaft 2 via the tenth gear the 25, the 11 gear 26, to drive output shaft, single output pinion 8, ring gear 9 and differential mechanism 10.
For second forward velocity of shifting gears from first forward velocity, first synchronizer 31 optionally engages with the 5th gear 17, is used for rotating jointly with jack shaft 6 so that connect the 5th gear 17.First drives clutch 4 disconnects from first input shaft 2, and second drives clutch 5 engages with second input shaft 3.Torque-flow from initial actuator to first input shaft 2 is interrupted.
When select second forward velocity than the time, from initial actuator to the end the torque-flow of actuator shown in Fig. 3 b.Moment of torsion transmits by four gear 16 and five gear 17 of second input shaft 3 via second gear train 15 from initial actuator, to drive the jack shaft 6 and first gear train 11, this first gear train comprises second gear 13 that is fixed on the jack shaft 6, around first gear 12 of first input shaft, 2 idle running be fixed on the 3rd gear 14 on the output shaft 7, to drive output shaft 7, output pinion 8, ring gear 9 and differential mechanism 10.Second gear train 15 is used to that moment of torsion is delivered to jack shaft 6, the first gear trains from second input shaft 3 and is used to via first gear 11 of idle running on first input shaft 2 moment of torsion is delivered to output shaft 7 from jack shaft 6.
For the 3rd forward velocity of shifting gears from second forward velocity, second synchronizer 33 optionally engages with the 9th gear 23 of the 4th gear train 21, is used for rotating jointly with output shaft 7 to connect the 9th gear 23.Second drives clutch 5 disconnects from second input shaft 3, and interrupting to the torque-flow of second input shaft 3, first drives clutch 4 engages with first input shaft 2.
In case select the 3rd forward velocity, moment of torsion is taken turns the 22 and the 9th gear 23 from initial actuator via the octadentate of first input shaft 2, the 4th gear train 21 and is delivered to output shaft 7, and be delivered to differential mechanism from output shaft 7 by output pinion 8 and ring gear 9, shown in Fig. 3 c.
For the 4th forward velocity ratio of shifting gears from the 3rd forward velocity ratio, the 4th synchronizer 34 optionally engages with the 7th gear 24, is used for rotating jointly with output shaft 7 to connect the 7th gear 24.First drives clutch 4 disconnects from first input shaft 2, interrupts the torque-flow from initial actuator to first input shaft 2 thus, and second drives clutch 5 engages with second input shaft 3.
Fig. 3 d shows the torque-flow that is used for the 4th forward velocity ratio.Be delivered to the 6th gear 19 and the 7th gear 20 of the 3rd gear train 18 from the moment of torsion of initial actuator by second input shaft 3, to drive output shaft 7 and differential mechanisms 10 via output pinion 8 and ring gear 9.
For the 5th forward velocity ratio of shifting gears from the 4th forward velocity ratio, the one-way synchronization device 32 that is installed on first input shaft 2 optionally engages with first gear 12 of first gear train 11.Second drives clutch 5 disconnects from second input shaft 3, and to interrupt the torque-flow from initial actuator to second input shaft 3, first drives clutch 4 engages with first input shaft 2, thereby initial actuator drives first input shaft 2 now.
When selecting the 5th forward velocity, shown in Fig. 3 e, moment of torsion is delivered to first gear 12 and the 3rd gear 14 of first gear train 11 from initial actuator by input shaft 2, to drive output shaft 7, output pinion 8, ring gear 9 and differential mechanism 10.Because first gear 12 also intermeshes with second gear 13 that is connected for jack shaft 6 common rotations, second gear 13 and jack shaft 6 dally when the 5th forward velocity is selected.
Reverse speed is provided than by double clutch 34 and reverse gear 27 are optionally engaged, thereby reverse gear 27 rotates jointly with output shaft 7.Second drives clutch 5 engages with second input shaft 3, and first drives clutch 4 disconnects from first input shaft 2.
Shown in Fig. 3 f, moment of torsion is delivered to the reverse gear 27 that be arranged on output shaft 7 on by second input shaft 3 via the 4th gear 16 and the 5th gear 17 of second gear train 15 from initial actuator, because reverse gear 27 and the 5th gear 17 intermesh.In case select the reverse speed ratio, be mounted for driving reverse gear 27 around the 4th gear 16 of second input shaft, 3 common rotations via the 5th gear 17 around jack shaft 6 idle running, this reverse gear optionally is connected to output shaft 7 and is used for rotating jointly with output shaft 7.
Fig. 4 a to 4f shows the speed changer 1 according to the 4th embodiment " '.Gear train is arranged identical with the 3rd embodiment with synchronizer.The 4th embodiment and the 3rd embodiment's difference is that the even number gear is attached to first input shaft 2, and the odd number gear is coupled to second input shaft 3.This layout with the 3rd embodiment is opposite.Reverse speed is than driving by second input shaft 3, as second with the 3rd embodiment's speed changer 1 ', 1 " the same.
In the 4th embodiment, first gear train 11 is used to provide first forward velocity ratio and the 5th forward velocity ratio.Second speed than provide by the 5th gear train 24, third speed than provide by the 3rd gear train 18, the 4th forward velocity is than providing by the 4th gear train 21.Reverse speed provides than by second gear train 15, as the second and the 3rd embodiment.
For with speed changer 1 " ' first forward velocity of shifting gears ratio, first synchronizer 31 optionally engages with the 5th gear 17, is used for rotating jointly with jack shaft 6 so that connect the 5th gear 17.Second drives clutch 5 engages with second input shaft 3, and first drives clutch 4 disconnects from first input shaft 3.Moment of torsion to first input shaft 2 is interrupted, and second input shaft 3 is driven by initial actuator.
When select first forward velocity than the time, torque-flow is shown in Fig. 4 a.Moment of torsion transmits by four gear 16 and five gear 17 of second input shaft 3 via second gear train 15 from initial actuator, to drive jack shaft 6.Jack shaft 6 drives output shafts 7 via first gear train 11, and this first gear train comprises second gear 13 that is fixed on the jack shaft 6, around first gear 12 of first input shaft, 2 idle running be fixed on the 3rd gear 14 on the output shaft 7.Output shaft 7 drives output pinion 8, ring gear 9 and differential mechanism 10.Second gear train 15 is used to that moment of torsion is delivered to jack shaft 6, the first gear trains 11 from second input shaft and is used to moment of torsion is delivered to output shaft 7 via first gear 11 that dallies from jack shaft 6 on first input shaft 2.
For second forward velocity ratio of shifting gears from first forward velocity ratio, the synchronizer 33 that is connected to output shaft 7 engages with the 11 gear 26 of the 5th gear train 24.Second drives clutch 5 disconnects from second input shaft 3, interrupts the torque-flow from initial actuator to second input shaft 3 thus, and first drives clutch 4 engages with first input shaft 3.
When select second forward velocity than the time, moment of torsion is delivered to output shaft 7 by second input shaft 2 via the tenth gear the 25, the 11 gear 26, to drive output shaft, single output pinion 8, ring gear 9 and differential mechanism 10, shown in Fig. 4 b.
For the 3rd forward velocity of shifting gears from second forward velocity, the 4th synchronizer 34 optionally engages with the 7th gear 24, is used for rotating jointly with output shaft 7 to connect the 7th gear 24.First drives clutch 4 disconnects from first input shaft 2, and second drives clutch 5 engages with second input shaft 3.
The torque-flow that is used for the 3rd forward velocity ratio is shown in Fig. 4 c.Be delivered to the 6th gear 19 and the 7th gear 20 of the 3rd gear train 18 from the moment of torsion of initial actuator by second input shaft 3, to drive output shaft 7 and differential mechanisms 10 via output pinion 8 and ring gear 9.
For the 4th forward velocity ratio of shifting gears from the 3rd forward velocity ratio, synchronizer 33 optionally engages with the 9th gear 22 of the 4th gear train 21, second drives clutch 5 disconnects from second input shaft 3, the torque-flow of interruption from final actuator to second input shaft 3, first drives clutch 4 engages with first input shaft 2.Initial actuator drives first input shaft 2 now.
Shown in Fig. 4 d, in case select the 3rd forward velocity, moment of torsion transmits via the octadentate of first input shaft 2, the 4th gear train 21 wheel the 22, the 9th gear 23 from initial actuator, driving output shaft 7, and is delivered to differential mechanism 10 from output shaft 7 by output pinion 8 and ring gear 9.
In order to be delivered to the 5th forward velocity ratio from the 4th forward velocity ratio, the synchronizer 32 that is connected to first input shaft 2 optionally engages with first gear 12 of first gear train 11.Second drives clutch 5 disconnects from second input shaft 3, and first drives clutch 4 engages with first input shaft 2.
The torque-flow that is used for the 5th forward velocity is shown in Fig. 4 e.Moment of torsion is delivered to first gear 12 and the 3rd gear 14 of first gear train 11 from initial actuator by input shaft 2, to drive output shaft 7, output pinion 8, ring gear 9 and differential mechanism 10.Because first gear 12 also intermeshes with second gear 13 that is connected for around jack shaft 6 common rotations, when selecting the 5th forward velocity, second gear 13 and jack shaft 6 idle running.
Reverse speed is provided than by double clutch 34 and reverse gear 27 are optionally engaged, thereby reverse gear 27 rotates jointly with output shaft 7.Synchronizer 31 on the jack shaft 6 disconnects from the 5th gear 17, thus 17 idle running of the 5th gear.Second drives clutch 5 engages with second input shaft 3, and first drives clutch 4 disconnects from first input shaft 2.
The torque-flow that is used for the reverse speed ratio illustrates at Fig. 4 f.Moment of torsion is delivered to the reverse gear 27 that be arranged on output shaft 7 on by second input shaft 3 via the 4th fixing gear 16 of second gear train 15 and the 5th gear 17 of pine from initial actuator, because reverse gear 27 and the 5th gear 17 intermesh, thereby reverse gear 27 drives output shaft 7.In case select the reverse speed ratio, be mounted for driving reverse gear 27 around the 4th gear 16 of second input shaft, 3 common rotations via the 5th gear 17 around jack shaft 6 idle running, this reverse gear optionally is connected to the output shaft 7 that is used for output shaft 7 common rotations.
Fig. 5 shows respectively the gear ratio that the speed changer in the embodiment shown in Fig. 2 a to 2f, 3a to 3f and the 4a to 4f 2 to 4 provides.
In all embodiments, the dual purpose of the setting of jack shaft 6 and first gear train 11 and second gear train 15 provides double-clutch speed changer, and it is compact and be specially adapted to limited especially miniature, the mini and compact car of free space.
Claims (15)
1. two clutch multi-speed transmission (1; 1 '; 1 "; 1 " '), it comprises:
Can be driven first input shaft (2) that clutch (4) engages by first,
Can be driven second input shaft (3) that clutch (5) engages by second,
Single output shaft (7),
Jack shaft (6),
Be used for jack shaft (6) can be attached to drivingly first torque transmission paths of output shaft (7), first torque transmission paths comprises first gear train (11), first gear train (11) comprise intermesh with second gear (13) and with intermeshing first gear of the 3rd gear (14) (12), first gear (12) is installed on first input shaft (2) or second input shaft (3), second gear (13) is installed on the jack shaft (6), and the 3rd gear (14) is installed on the output shaft (7).
2. as claimed in claim 1 pair of clutch multi-speed transmission (1; 1 '; 1 "; 1 " '), wherein
First gear (12) is connected for around first input shaft (2) or second input shaft (3) rotation, and second gear (13) is connected for around the common rotation of jack shaft (6), and the 3rd gear (14) is connected for around the common rotation of output shaft (7).
3. as claimed in claim 1 or 2 pair of clutch multi-speed transmission (1; 1 '; 1 "; 1 " '); also comprise second torque transmission paths; be used for first input shaft (2) or second input shaft (3) can be connected to jack shaft (6) drivingly; second torque transmission paths comprises and first gear train (11) at interval second gear train (15) axially; second gear train (15) comprises the 4th gear (16) and the 5th gear (17); the 4th gear is connected for rotating jointly around first input shaft (2) or second input shaft (3), the 5th gear is connected for around jack shaft (6) rotation, first torque-transmitting mechanisms (28; 31), it selectively engages so that the 5th gear (17) is connected to jack shaft (6), is used to make the common rotation of the 5th gear and jack shaft (6).
4. as each the described pair of clutch multi-speed transmission (1 in the claim 1 to 3; 1 '; 1 "; 1 " '), also comprises second torque-transmitting mechanisms (29; 32), it selectively engages first gear (12) is connected to first input shaft (2) or second input shaft (3), is used for and first input shaft (2) or the common rotation of second input shaft (3).
5. as claim 3 or 4 described pairs of clutch multi-speed transmissions (1; 1 '; 1 "; 1 " '), wherein,
The 5th gear (17) intermeshes with the reverse gear (27) that is connected for around output shaft (7) rotation.
6. as each the described pair of clutch multi-speed transmission (1) in the claim 3 to 5, wherein
First gear (12) is connected for around second input shaft (3) rotation, and the 4th gear (16) is connected for around the common rotation of first input shaft (2).
7. as claimed in claim 6 pair of clutch multi-speed transmission (1), also comprise the 3rd gear train (21), itself and first gear train (11) and second gear train (15) are axially at interval, the 3rd gear train (21) comprises the 7th gear (23) that is connected for common the 6th gear (22) that rotates of first input shaft (2) and is connected for rotating around jack shaft (6).
8. as each the described pair of clutch multi-speed transmission (1 ' in the claim 3 to 5; 1 "), wherein,
First gear (12) is connected for around first input shaft (2) rotation, and the 4th gear (16) is connected for and the common rotation of second input shaft (3).
9. as each the described pair of clutch multi-speed transmission in the claim 3 to 5 (1 " '), wherein,
First gear (12) is connected for around second input shaft (3) rotation, and the 4th gear (16) is connected for and the common rotation of second input shaft (3).
10. as each the described pair of clutch multi-speed transmission (1) in the claim 1 to 7, wherein,
Be provided with three double-direction twist moment transfer mechanisms (28,29,30), wherein, a double-direction twist moment transfer mechanism (28) is connected to jack shaft (6), a double-direction twist moment transfer mechanism (29) is connected to second input shaft (3), and a double-direction twist moment transfer mechanism (30) is connected to output shaft (7).
11. two as claimed in claim 8 or 9 clutch multi-speed transmissions (1 '; 1 "; 1 " '), wherein,
Two unidirectional torque transfer mechanisms (31,32) and two double-direction twist moment transfer mechanisms (33,34) are set, and wherein, a unidirectional torque transfer mechanism (31) is connected to jack shaft (6).
12. the as claimed in claim 11 pair of clutch multi-speed transmission (1 "; 1 " '), wherein,
A double-direction twist moment transfer mechanism (33) is connected to first input shaft (2), and a double-direction twist moment transfer mechanism (34) and a unidirectional torque transfer mechanism (32) are connected to output shaft (7).
13. as claimed in claim 11 pair of clutch multi-speed transmission (1 '), wherein,
A unidirectional torque transfer mechanism (32) is connected to first input shaft (2), and two double-direction twist moment transfer mechanisms (33,34) are connected to output shaft (7).
14. as each described pair of clutch multi-speed transmission (1 in the claim 1 to 13; 1 '; 1 "; 1 " '), wherein,
Double-clutch speed changer provides five forward velocity ratios and a reverse speed ratio.
15. a vehicle comprises as each described pair of clutch multi-speed transmission (1 in the claim 1 to 14; 1 '; 1 "; 1 " ').
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB1000608.8 | 2010-01-14 | ||
| GB201000608A GB2476956A (en) | 2010-01-14 | 2010-01-14 | Dual clutch multi-speed transmission and vehicle having a dual clutch multi-speed transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102128237A true CN102128237A (en) | 2011-07-20 |
Family
ID=42028377
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011100045329A Pending CN102128237A (en) | 2010-01-14 | 2011-01-11 | Dual clutch multi-speed transmission and vehicle having a dual clutch multi-speed transmission |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN102128237A (en) |
| GB (1) | GB2476956A (en) |
| RU (1) | RU2011101360A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011056517A1 (en) * | 2011-12-16 | 2013-06-20 | Fev Gmbh | Transmission for a motor vehicle and method for controlling such a transmission |
| GB201605063D0 (en) | 2016-03-24 | 2016-05-11 | Qinetiq Ltd | A transmission |
| RU189828U1 (en) * | 2018-12-05 | 2019-06-05 | Виктор Анатольевич Фомичев | TRANSMISSION MINI-BAGGY |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1122422A (en) * | 1994-10-31 | 1996-05-15 | 格特拉格传动机构和齿轮厂黑曼·哈根梅尔有限公司 | Mehrgang-stufengetriebe a stepper motor vehicle transmission |
| DE10015336A1 (en) * | 2000-03-28 | 2001-10-04 | Volkswagen Ag | Dual clutch gearbox has elements arranged so that for certain engaged gear drive train consists of first drive shaft, parallel shaft, second input shaft and output shaft |
| CN1779292A (en) * | 2005-06-24 | 2006-05-31 | 重庆青山工业有限责任公司 | Multiple-gear speed variator of vehicle |
| WO2006125876A1 (en) * | 2005-05-20 | 2006-11-30 | Pascal Thery | Double-clutch gearbox |
| CN1957193A (en) * | 2004-03-24 | 2007-05-02 | 安东诺夫汽车技术有限公司 | Motor vehicle gearbox, in particular with a twin-clutch |
| GB2458801A (en) * | 2008-03-31 | 2009-10-07 | Gm Global Tech Operations Inc | Dual clutch transmission with chain drive between input shaft and layshaft |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006054271A1 (en) * | 2006-11-17 | 2008-06-12 | Zf Friedrichshafen Ag | Double clutch transmission of a motor vehicle |
| US7748286B2 (en) * | 2007-04-03 | 2010-07-06 | Ford Global Technologies, Llc | Dual clutch transmission having reduced axial length |
-
2010
- 2010-01-14 GB GB201000608A patent/GB2476956A/en not_active Withdrawn
-
2011
- 2011-01-11 CN CN2011100045329A patent/CN102128237A/en active Pending
- 2011-01-13 RU RU2011101360/11A patent/RU2011101360A/en not_active Application Discontinuation
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1122422A (en) * | 1994-10-31 | 1996-05-15 | 格特拉格传动机构和齿轮厂黑曼·哈根梅尔有限公司 | Mehrgang-stufengetriebe a stepper motor vehicle transmission |
| DE10015336A1 (en) * | 2000-03-28 | 2001-10-04 | Volkswagen Ag | Dual clutch gearbox has elements arranged so that for certain engaged gear drive train consists of first drive shaft, parallel shaft, second input shaft and output shaft |
| CN1957193A (en) * | 2004-03-24 | 2007-05-02 | 安东诺夫汽车技术有限公司 | Motor vehicle gearbox, in particular with a twin-clutch |
| WO2006125876A1 (en) * | 2005-05-20 | 2006-11-30 | Pascal Thery | Double-clutch gearbox |
| CN1779292A (en) * | 2005-06-24 | 2006-05-31 | 重庆青山工业有限责任公司 | Multiple-gear speed variator of vehicle |
| GB2458801A (en) * | 2008-03-31 | 2009-10-07 | Gm Global Tech Operations Inc | Dual clutch transmission with chain drive between input shaft and layshaft |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2011101360A (en) | 2012-07-20 |
| GB2476956A (en) | 2011-07-20 |
| GB201000608D0 (en) | 2010-03-03 |
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Application publication date: 20110720 |