CN102192282A - Dual clutch transmission - Google Patents
Dual clutch transmission Download PDFInfo
- Publication number
- CN102192282A CN102192282A CN2011100716342A CN201110071634A CN102192282A CN 102192282 A CN102192282 A CN 102192282A CN 2011100716342 A CN2011100716342 A CN 2011100716342A CN 201110071634 A CN201110071634 A CN 201110071634A CN 102192282 A CN102192282 A CN 102192282A
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- China
- Prior art keywords
- gear
- driven
- actuation
- group
- driven gear
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
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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
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
Abstract
The invention relates to a dual clutch transmission. The dual clutch transmission has a reverse gear driven by a reverse driving gearwheel via an intermediate idler wheel freely rotatably mounted on an intermediate lay shaft, which avoids the need for a long intermediate lay shaft. The driving gearwheel, the intermediate idler wheel and the reverse driving gearwheel are aranged on the same plane. The transmission has a driving gearwheel and a driven gearwheel for first gear disposed on their respective input and output shafts at or near a centre of the transmission near a region on the output shaft where shaft bending is high. This is intended to minimise misalignment between gear meshes of the driving gearwheel and the driven gearwheel for first gear caused by flexure in the wheels, thereby reducing wear and noise as the gear meshes more efficiently enqage with each other. The low speed, high loaded gears (Gl/RG, G2; Gl, G2/RG) are disposed so that they alternate with the higher speed, lower loaded gears (G6/G4, G5/G3), thereby distributing load evenly along the shaft and reducing a likelihood of shaft fatigue.
Description
Technical field
The present invention relates to double-clutch speed changer.
Background technique
In double-clutch speed changer, each clutch all is connected with the input shaft that has fixed drive wheel, this driving wheel with corresponding idle pulley on the axle is engaged.Selector operation with one of them idle pulley with axle is fixed, thereby by clutch to the axle transmission of drive force.
This means, when selecting one of them by this way to one of them idle pulley on the axle, can the next gear of select progressively with another selector that axle is associated, when with this during, can finish stably gear and change the corresponding clutch of axle.This means that one carries odd gear to bearing, and another will carry the even number gear.
The position of reverse gear and mode of operation thereof have multiple different design, and in general design comprises the idler shaft that connects by second gear.This can cause the undesirable increase of transmission dimensions usually.
Two gears of the load maximum of carrying are one grade and reverse gear.In order to reduce to install the influence to bending shaft of these two gears as far as possible, these two gears generally are positioned at these a end or near the other end (disclosed as US4461188, DE19821164, US7426880 etc.).Similarly, third gear, fourth gear, five grades and six grades of general these intermediate portions that all are positioned to axle.
High capacity gear (second gear, one grade and reverse gear) often is positioned at gear dislocation and the consequent high contact stress that these layouts at shaft end place is had amplitude peak, and this has increased the possibility of gear fatigue.
Summary of the invention
From the above mentioned, though need in the industry a kind of also can be when high capacity with the maximized double-clutch speed changer of the engagement between actuation gear and the driven gear, also need and can under the prerequisite that does not increase the design overall dimensions, allow reverse gear to have the ability of more gears.
Double-clutch speed changer well known in the prior art has two clutches that are mechanically connected to prime mover by traditional approach through live axle.Each clutch also with corresponding concentric input shaft mechanical connection, according to the difference of selected clutch, the driving force of motor is applied to wherein on the input shaft.Two output shafts are provided with abreast with respect to input shaft.Each input shaft carries one group of fixing actuation gear, and the corresponding rotatable driven idle pulley group of being carried on these actuation gears and the output shaft meshes.Coupling arrangement can be selected the idle pulley gear, and they are held in place on the corresponding output shaft, rotates output gear thus, thus propelled vehicles.
Double-clutch speed changer among the present invention is avoided needs to long middle countershaft by one in the actuation gear through be installed in middle idler gear wheel drive on the middle countershaft that is used for reverse gear free to rotately by making one group of idle pulley gear in the driven idle pulley gear.
Double-clutch speed changer among the present invention makes because one grade actuation gear and the dislocation of the engagement between the driven gear of being used for that tooth bending produces minimizes, thereby reduces wear the reduction noise because gear more effectively is engaged with each other.This be by will be used for one grade actuation gear and driven gear be arranged at the speed changer center or near the center separately input shaft and output shaft on realize.
Double-clutch speed changer among the present invention passes through low speed, high capacity gear (G1/RG, G2; G1, G2/RG) be arranged to at a high speed, (G6/G4 G5/G3) replaces and reduces the tired probability of axle low load gear.Employed gear spacing can be optimized the load distribution along axle among the present invention, thereby helps to reduce the tired possibility of axle.
Description of drawings
In order more completely to explain the present invention and technological merit thereof, with reference to following explanation and accompanying drawing, in the accompanying drawing:
Fig. 1 is the schematic representation of arranging of six fast double-clutch speed changers;
Fig. 2 is the schematic representation of arranging of seven fast double-clutch speed changers;
Fig. 3 A and 3B illustrate the operation of reverse gear in the six speed transmission; And
Fig. 4 A and 4B illustrate the operation of reverse gear in the seven speed transmission.
Embodiment
Fig. 1 to Fig. 3 illustrates the representative schematic representation of double-clutch speed changer 100 of the present invention, referring to figs. 1 to Fig. 3, can understand embodiments of the present invention and technological merit thereof better.
First clutch K1 and second clutch K2 are by live axle 102 and prime mover 104 mechanical connection in a conventional manner.Each clutch also with first input shaft 106 and second input shaft, 108 mechanical connections.Second input shaft is concentric with first input shaft.Therefore, according to selected clutch, the driving force of motor is applied in wherein on the input shaft.Fixing actuation gear 134,136 is connected with first input shaft, and fixing actuation gear 138,140 is connected with second input shaft.First output shaft 110 and second output shaft 112 are provided with abreast with respect to input shaft.Driven idle pulley gear 118,120,122; 120,118,116,122 are positioned on first output shaft, and driven idle pulley gear 124,126,128,130 is positioned on second output shaft.Coupling arrangement 146,148,150,152 can be selected the idle pulley gear, and they are fixed on the corresponding output shaft, rotates output gear 142,144 thus, thus propelled vehicles.These aspects are that prior art is known.
What have novelty with respect to prior art is special distribution to the velocity ratio of stationary drive gear and idle pulley gear.If fixing actuation gear and corresponding idle pulley gear thereof and that the axle of these gears is installed is firm inadequately, so when applying high load they with bending.Close and high capacity to occur with the corresponding fixing actuation gear of reverse gear/idler gear wheels with one grade.This situation can be by the diameter of increase input shaft and output shaft or by avoiding at the bearing end place near axle with the corresponding positioning parts of reverse gear with one grade.But this does not overcome the problem of fixing actuation gear and idle pulley tooth bending.Increase the fixing actuation gear and the thickness of idle pulley gear and can reduce bending, but will increase the size and the weight of speed changer like this.We have found that, if fixing actuation gear/idle pulley Gear combination that will be corresponding with one grade and reverse gear be positioned on the serious point of bending shaft on the axle or this point near, the bending of the correspondence by gear can make the engagement of actuation gear/idle pulley Gear combination misplace to minimize so.
Therefore, be clearly shown that fixing actuation gear 138 and driven idle pulley gear 128 engagement, i.e. one grade of G1 by Fig. 1.Idle pulley gear 128 also meshes with the middle idle pulley gear 132 that is installed on the middle countershaft 114, and middle idle pulley gear 132 meshes with the driven idle pulley gear 120 of reverse gear again, forms reverse gear.Because mating surface more effectively is engaged with each other, thus this one grade be installed near the layout axle central authorities or the central authorities advantageously reduced wearing and tearing, reduce noise.Like this, one grade of G1 and reverse gear RG are positioned as by same driving gear drives, and can engage and separate by interconnected coupling arrangement 148,152.Such words just need not to invent the same long reverse gear idler shaft that uses with other this type of, makes that layout is compacter.One grade of G1 and reverse gear RG be arranged in be near another benefit the axle central authorities, low speed, high capacity gear R1/RG, R2 can be oriented to at a high speed, low load gear G6/G4, G5/G3 alternately, thereby reduce the tired probability of axle.
Fig. 1 illustrates of the present invention six fast gear-boxes, and wherein actuation gear 136,138,140 all meshes with two idle pulley gears 118/126,120/128,122/130, and actuation gear 134 only meshes with idle pulley gear 124.By introducing the possibility of more gears, can make originally arranges has other features.Thus, with reference to figure 2, seven so fast gear-boxes are shown, reverse gear RG and second gear G2 relatively locate, and introduce another gear G7 in the original position of reverse gear relative with one grade of G1.Because mating surface more effectively is engaged with each other, the central authorities or the reducing wear of central vicinity of axle are reduced the advantage of noise so the reservation of this layout is installed in one grade of G1.This layout also allows low speed, high capacity gear to replace with high speed, low load gear, thereby reduces the probability of axle fatigue.Simultaneously, the size of this layout is identical with six speed transmission, but can advantageously provide seven speed transmission.
Can understand the operation of reverse gear in the six speed transmission better with reference to figure 3A and 3B.These figure provide from the speed changer view of differential gear 154 directions.The plane of dot and dash line correspondence differential gear 154 among Fig. 3 A and the 3B and two output gears 142,144 that are attached thereto usually.The corresponding fixing actuation gear 138 of solid line among Fig. 3 A and the 3B and the plane of the driven idle pulley gear 120,128,132 of correspondence.The actuation gear 138 that is fixedly mounted on first input shaft 106 passes through first clutch K1 reception driving force, and meshes and make their rotations with the driven middle idle pulley gear 132 that is rotatably installed in the driven idle pulley gear 128 on second output shaft 112 and be rotatably installed on the middle countershaft 114.Idle pulley gear 132 also meshes with the driven idle pulley gear 120 of reverse gear that is rotatably installed on first output shaft 110 in the middle of driven.Gu Ding actuation gear 138 provides driving force for one grade of G1 and reverse gear RG thus.
When coupling arrangement 152 engaged with driven gear 128, driving force was passed to output shaft 112 by input shaft 106, makes output gear 144 rotate with direction as shown, thereby forward drive power is passed to differential gear 154.Under this situation, drive path is:
138 → 128-[152 on K2 → 106] 144 → 154 on-112 → 112
When coupling arrangement 152 separates and coupling arrangement 148 when engaging, driving force is passed to output shaft 110 by input shaft 106 by idle pulley gear 132 in the middle of driven, makes output gear 142 rotate with direction as shown, thereby reverse-drive power is passed to differential gear 154.Under this situation, drive path is:
132 → 120-[148 on K2 → 106 138 → 114] 142 → 154 on-110 → 110
The operation of the reverse gear of seven speed transmission is similar with it, referring to Fig. 4 A and 4B, and the plane of actuation gear 134 that wherein solid line is corresponding fixing and corresponding driven idle pulley gear 120,124,132.Gu Ding actuation gear 134 provides driving force for second gear R2 and reverse gear RG thus.
These layouts mean actuation gear 138,134, driven middle idle pulley gear 132 and the driven idle pulley gear 120 of reverse gear all at grade, thereby make the transmission of torque maximization.
Claims (8)
1. double-clutch speed changer (100) with at least six gears comprising:
A) second input shaft (108) in first input shaft (106) of the inboard that is provided with coaxially to each other and can rotates and the outside;
B) can be connected to the first clutch and the second clutch (K1 of the live axle (102) of prime mover (104), K2), described first clutch (K1) drives described first input shaft (106), and described second clutch (K2) then is used to drive described second input shaft (108);
First output shaft (110) that c) can rotate, second output shaft (112) and middle countershaft (114);
D) first group of actuation gear (138,140) that also can therewith rotate by described first input shaft (106) carrying;
E) second group of actuation gear (134,136) that also can therewith rotate by described second input shaft (108) carrying;
F) can be installed in first group of driven gear (118,120,122 on described first output shaft (110) freely to rotate; 120,118,116,122), each in described first group of driven gear is by corresponding described actuation gear (136,138,140; 134,136,138,140) drive to rotate, to obtain specific gear, each in described first group of driven gear is associated with corresponding coupling arrangement (146,148), with optionally with the transmission of torque of described driven gear to described first output shaft;
G) can be installed in second group of driven gear (124 on described second output shaft (112) freely to rotate, 126,128,130), in described second group of driven gear each is by corresponding described actuation gear (134,136,138,140) drive rotation, to obtain specific gear, in described second group of driven gear each is associated with corresponding coupling arrangement (150,152), with optionally with the transmission of torque of described driven gear to described second output shaft; And
H) be arranged on first output gear (142) on described first output shaft and be arranged on second output gear (144) on described second output shaft, described first output gear and second output gear engage with differential gear, make the torque of the described actuation gear on the described input shaft optionally be changed and export;
It is characterized in that, gear (120) in described first group of driven gear is by described actuation gear (138,134) in one is used for by being installed in freely to rotate that middle the idle pulley gear (132) on the countershaft drives in the middle of reverse gear (RG) described, thereby does not need the middle countershaft grown;
And be characterised in that, described first group of actuation gear comprises first actuation gear (138) that is associated with a grade (G1) at least, and described second group of driven gear comprise can with first driven gear (128) of described first actuation gear engagement that is used for a grade (G1), it is arranged on described first input shaft and described second output shaft in speed changer central authorities or near the speed changer centre respectively, thereby make because described first actuation gear that tooth bending produces and the dislocation of the gear engagement between described first driven gear minimize, reduce wearing and tearing and noise thus because gear more effectively is engaged with each other.
2. double-clutch speed changer according to claim 1, wherein said gear (120) is driven by described first actuation gear (138), thereby make because the gear engagement dislocation of described first actuation gear that tooth bending produces and described gear (120) minimizes, thereby reduce wearing and tearing and noise because gear more effectively is engaged with each other.
3. according to the double-clutch speed changer of arbitrary aforementioned claim, wherein said first group of actuation gear comprises second actuation gear (140) that is associated with two gears (G3 and G5).
4. according to the double-clutch speed changer of arbitrary aforementioned claim, wherein said second group of actuation gear comprises the 3rd actuation gear (134) that is associated with second gear (G2) at least and the 4 wheel driven moving gear (136) that is associated with two gears (G4 and G6).
5. according to the double-clutch speed changer of arbitrary aforementioned claim, wherein said first group of driven gear comprise can with second driven gear (122) of second actuation gear engagement that is used for five grades (G5) and can with the 3rd driven gear (118) of the 3rd actuation gear engagement that is used for six grades (G6).
6. according to the double-clutch speed changer of arbitrary aforementioned claim, wherein said second group of driven gear comprise can with the 4th driven gear (130) of second actuation gear engagement that is used for third gear (G3), can with the 5th driven gear (126) of the 3rd actuation gear engagement that is used for fourth gear (G4) and can with the 6th driven gear (124) of the 4 wheel driven moving gear engagement that is used for second gear (G2).
7. according to claim 1, each described double-clutch speed changer in 3,4,5,6, wherein said first group of driven gear comprise can with the 7th driven gear (122) of first actuation gear engagement that is used for seven grades (G7).
8. according to the double-clutch speed changer of arbitrary aforementioned claim, the gear of low speed, high capacity (G1/RG, G2 wherein; G1, G2/RG) be configured to at a high speed, the gear of low load (G6/G4, G5/G3) alternately, thereby make on the axle load allocating evenly and reduce the tired possibility of axle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910022655.1A CN109737188A (en) | 2010-03-19 | 2011-03-21 | Double-clutch speed changer |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB201004606A GB2478785B (en) | 2010-03-19 | 2010-03-19 | Dual clutch transmission |
| GB1004606.8 | 2010-03-19 |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910022655.1A Division CN109737188A (en) | 2010-03-19 | 2011-03-21 | Double-clutch speed changer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102192282A true CN102192282A (en) | 2011-09-21 |
Family
ID=42227991
Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200792267U Expired - Lifetime CN202082350U (en) | 2010-03-19 | 2011-03-21 | Dual-clutch transmission |
| CN201910022655.1A Pending CN109737188A (en) | 2010-03-19 | 2011-03-21 | Double-clutch speed changer |
| CN2011100716342A Pending CN102192282A (en) | 2010-03-19 | 2011-03-21 | Dual clutch transmission |
Family Applications Before (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200792267U Expired - Lifetime CN202082350U (en) | 2010-03-19 | 2011-03-21 | Dual-clutch transmission |
| CN201910022655.1A Pending CN109737188A (en) | 2010-03-19 | 2011-03-21 | Double-clutch speed changer |
Country Status (2)
| Country | Link |
|---|---|
| CN (3) | CN202082350U (en) |
| GB (1) | GB2478785B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105276101A (en) * | 2014-07-02 | 2016-01-27 | 现代自动车株式会社 | Automated manual transmission |
| CN105351504A (en) * | 2015-12-01 | 2016-02-24 | 重庆蓝黛动力传动机械股份有限公司 | Automobile transmission reverse gear mechanism |
| CN106795959A (en) * | 2014-10-06 | 2017-05-31 | 五十铃自动车株式会社 | The control device and control method of double disengaging type speed changers |
| CN107725761A (en) * | 2016-08-11 | 2018-02-23 | 上海汽车集团股份有限公司 | The fork controls method, apparatus and automobile of the double disengaging type speed changers of wet type |
| CN107867169A (en) * | 2016-09-28 | 2018-04-03 | 比亚迪股份有限公司 | Power-driven system and vehicle for vehicle |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2478785B (en) * | 2010-03-19 | 2013-01-30 | Romax Technology Ltd | Dual clutch transmission |
| CN107738170A (en) * | 2017-11-16 | 2018-02-27 | 江门市兄弟机械制造有限公司 | A kind of foot-operated protection polishing machine of more power |
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| GB2369656A (en) * | 2000-11-21 | 2002-06-05 | Luk Lamellen & Kupplungsbau | Automatic transmission hydraulic actuation system having an isolating valve which prevent leaks |
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| CN1621715A (en) * | 2003-11-27 | 2005-06-01 | 现代自动车株式会社 | Double clutch transmission |
| WO2005093289A1 (en) * | 2004-03-17 | 2005-10-06 | Daimlerchrysler Ag | Double-clutch gearbox |
| CN101535679A (en) * | 2006-11-17 | 2009-09-16 | Zf腓德烈斯哈芬股份公司 | Double clutch transmission of a motor vehicle |
| CN101614266A (en) * | 2009-07-27 | 2009-12-30 | 杨军 | Double clutch is multi-functional six speed transmissions of symmetric arrangement |
| CN202082350U (en) * | 2010-03-19 | 2011-12-21 | 诺迈士科技有限公司 | Dual-clutch transmission |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7669497B2 (en) * | 2006-08-23 | 2010-03-02 | Gm Global Technology Operations, Inc. | Powertrain with torque converter and axially compact seven speed dual clutch transmission |
| EP2055989B1 (en) * | 2007-10-29 | 2010-12-15 | Ford Global Technologies, LLC | A double clutch transmission |
| US8056429B2 (en) * | 2008-04-02 | 2011-11-15 | GM Global Technology Operations LLC | Multi-speed dual clutch transmission with countershaft gearing arrangement |
-
2010
- 2010-03-19 GB GB201004606A patent/GB2478785B/en active Active
-
2011
- 2011-03-21 CN CN2011200792267U patent/CN202082350U/en not_active Expired - Lifetime
- 2011-03-21 CN CN201910022655.1A patent/CN109737188A/en active Pending
- 2011-03-21 CN CN2011100716342A patent/CN102192282A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2369656A (en) * | 2000-11-21 | 2002-06-05 | Luk Lamellen & Kupplungsbau | Automatic transmission hydraulic actuation system having an isolating valve which prevent leaks |
| US6568515B2 (en) * | 2000-11-21 | 2003-05-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydraulic actuation systems |
| DE10108881A1 (en) * | 2001-02-23 | 2002-09-05 | Volkswagen Ag | Dual clutch gearbox has two gearbox parts and single shift shaft axially displaced and rotated by selection actuator and shift actuator with shift shaft connecting to shift rod of one gearbox part without disengaging previously engaged gear |
| CN1621715A (en) * | 2003-11-27 | 2005-06-01 | 现代自动车株式会社 | Double clutch transmission |
| WO2005093289A1 (en) * | 2004-03-17 | 2005-10-06 | Daimlerchrysler Ag | Double-clutch gearbox |
| CN101535679A (en) * | 2006-11-17 | 2009-09-16 | Zf腓德烈斯哈芬股份公司 | Double clutch transmission of a motor vehicle |
| CN101614266A (en) * | 2009-07-27 | 2009-12-30 | 杨军 | Double clutch is multi-functional six speed transmissions of symmetric arrangement |
| CN202082350U (en) * | 2010-03-19 | 2011-12-21 | 诺迈士科技有限公司 | Dual-clutch transmission |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105276101A (en) * | 2014-07-02 | 2016-01-27 | 现代自动车株式会社 | Automated manual transmission |
| CN105276101B (en) * | 2014-07-02 | 2019-07-12 | 现代自动车株式会社 | Auto-manual speed changer |
| CN106795959A (en) * | 2014-10-06 | 2017-05-31 | 五十铃自动车株式会社 | The control device and control method of double disengaging type speed changers |
| CN106795959B (en) * | 2014-10-06 | 2018-10-16 | 五十铃自动车株式会社 | The control device and control method of double disengaging type speed changers |
| US10145468B2 (en) | 2014-10-06 | 2018-12-04 | Isuzu Motors Limited | Control device and control method for dual clutch-type transmission |
| CN105351504A (en) * | 2015-12-01 | 2016-02-24 | 重庆蓝黛动力传动机械股份有限公司 | Automobile transmission reverse gear mechanism |
| CN107725761A (en) * | 2016-08-11 | 2018-02-23 | 上海汽车集团股份有限公司 | The fork controls method, apparatus and automobile of the double disengaging type speed changers of wet type |
| CN107867169A (en) * | 2016-09-28 | 2018-04-03 | 比亚迪股份有限公司 | Power-driven system and vehicle for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| GB201004606D0 (en) | 2010-05-05 |
| CN109737188A (en) | 2019-05-10 |
| GB2478785B (en) | 2013-01-30 |
| GB2478785A (en) | 2011-09-21 |
| CN202082350U (en) | 2011-12-21 |
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Application publication date: 20110921 |