CN102966706A - Three-shaft double-clutch speed changer - Google Patents
Three-shaft double-clutch speed changer Download PDFInfo
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- CN102966706A CN102966706A CN2012105019151A CN201210501915A CN102966706A CN 102966706 A CN102966706 A CN 102966706A CN 2012105019151 A CN2012105019151 A CN 2012105019151A CN 201210501915 A CN201210501915 A CN 201210501915A CN 102966706 A CN102966706 A CN 102966706A
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Abstract
The invention belongs to a speed changer, and particularly relates to a three-shaft double-clutch speed changer. The speed changer is characterized in that the speed changer comprises two clutches, two input shafts and an output shaft, wherein the two clutches are driven by gear transmission or belt transmission by an engine and connected with the corresponding input shafts respectively; an odd-gear driving gear set is arranged on one input shaft; an even-gear driving gear set is arranged on the other input shaft; a driven gear set is arranged on the output shaft; driving gears of the two input shafts share the corresponding driven gears; reverse gear driving gears are arranged on one input shaft; reverse gear driven gears are arranged on the other input shaft and engaged with the reverse gear driving gears; the soldered tooth ring part of a parking mechanism is fixedly connected with a box body; and the parking mechanism is matched with an output shaft synchronizer and achieves a parking function by pulling a shifting fork with gear shifting stay wire. The speed changer is compact in structure, the cost is lowered, the axial length of the speed changer is shortened as no coaxial shaft is adopted, the system rigidity is improved, and the performance is reliable.
Description
Technical field
The invention belongs to transmission-like, specifically a kind of three axle dual-clutch transmissions.
Background technique
Dual-clutch transmission switches by the coupling of two clutches realizes the gearshift action, and gearshift rapidly steadily.In shift process, the power of motor constantly is passed on the wheel all the time, realizes power gear shifting, guarantees that vehicle has good acceleration performance.Double-clutch speed changer develops based on the parallel-axis type manual transmission, and it has inherited many advantages such as the manual transmission transmission efficiency is high, installing space is compact, quality is light, price is low.
The dual-clutch transmission structure mainly contains three kinds at present: the output of double clutch single shaft, the output of combined clutch single shaft and the output of combined clutch twin shaft.The output of double clutch single shaft has utilized existing equipment and technology to greatest extent, and is suitable with manual transmission component machining difficulty, effectively reduces development cost.Compare this structure with manual transmission and can make transmission shaft to shorten length, system stiffness improves, and still, the height of speed changer increases, and requires to reserve relatively large arrangement space into speed changer.
Combined clutch single shaft export structure is compact, and footprint is little, is applicable to the limited speed changer of arrangement space.But high to the accuracy of manufacturing of combined clutch and driving-shaft assembly component and life requirements, also need solve simultaneously the technical problems such as the cooperation of combined assembly and heat radiation.The basic utilization ratio of original MT component is restricted, so development cost is relatively high.
The speed changer axial length has been shortened in the output of combined clutch twin shaft, effectively improve system stiffness, be applicable to the less complete machine structure of axial dimension requirement, identical with double clutch single shaft export structure, also exist technological difficulties and the high development cost same with the coaxial output of double clutch.The same with double clutch single shaft export structure, require to reserve relatively large arrangement space into speed changer.
Double clutch system has dry clutch and two kinds of forms of wet clutch.Dry type diaphragm spring single plate clutch have the secondary part rotary inertia little, simple in structure, easy to adjust, separate thoroughly, the torque overload protection, efficient is high, cost is lower, do not need the advantage such as auxiliary power.Dry clutch absorbs larger heat by pressing plate and flywheel, and the speed that sliding wear is produced heat is insensitive, but the air heat radiation is slower, and heat is difficult for distributing at short notice, so it is subjected to the total heat quantitative limitation of sliding wear generation.
Wet clutch has preferably controllability and control quality, and structure is more single, have pressure distribution evenly, wearing and tearing are little and even, the transmitting torque capacity large, need not adjust specially the characteristics such as friction plate gap.Because it forces cooling with hydraulic oil, skid for a long time when allowing starting and high gear starting and can scaling loss lining face, be widely used on the clutch of Modern Automotive Automatic Transmissions.But be between the driving and driven friction plate of the multidisc clutch in the separated state because mutually trackslipping through lubricant oil, produce larger surface friction drag, make the corresponding reduction of transmission efficiency of speed changer.
Summary of the invention
Purpose of the present invention provides a kind of dual input shaft, compact structure, cooperates the three axle dual-clutch transmissions of realizing Parking without the synchronizer on the idle pulley that reverses gear, the employing output shaft with the joint gear ring that casing is connected for the deficiencies in the prior art.
The present invention realizes by following technical proposal:
A kind of three axle dual-clutch transmissions, it is characterized in that: comprise two clutches, two input shafts, an output shaft, power drives two clutches by motor with gear transmission or with the mode of transmission, two clutches are continuous with corresponding input shaft respectively, arrange odd number gear driving tooth wheels on the input shaft, arrange even number gear driving tooth wheels on another root input shaft; Arrange the driven tooth wheels on the output shaft, the driving gear of two input shafts shares corresponding driven gear, and the driving gear that reverses gear is arranged on wherein on the input shaft, and the driven gear that reverses gear is arranged on another root input shaft, and driving gear meshes with reversing gear.
One gear driving gear of odd number gear driving tooth wheels of the present invention, three gear driving gears, five gear driving gears, seven gear driving gears and the driven gear that reverses gear are arranged on the first input shaft; Two gear driving gears of even number gear driving tooth wheels, four gear driving gears, six gear driving gears and the driving gear that reverses gear are arranged on the second input shaft; Five gear driving gears are connected by the first synchronizer with three gear driving gears, seven gear driving gears are connected with the second synchronizer, four gear driving gears are connected by the 3rd synchronizer with two gear driving gears, six gear driving gears are connected by the 4th synchronizer with the driving gear that reverses gear, and the first driven gear of driven tooth wheels, the second driven gear, the 3rd driven gear and the 4th driven gear are arranged on the output shaft; The first driven gear and a gear driving gear engagement; The second driven gear and two gear driving gears, three gear driving gear engagements; The 3rd driven gear and four gear driving gears, five gear driving gear engagements; The 4th driven gear and six gear driving gears, seven gear driving gear engagements; The driven gear and three that reverses gear keeps off driving gears and connects firmly, reverse gear driven gear and the driving gear engagement of reversing gear, and the output shaft synchronous device connects the first driven gear.The joint gear ring of halting mechanism of the present invention and casing connect firmly or be designed to can not be around output shaft rotation, and it cooperates with the output shaft synchronous device, realizes parking function by gear-shifting bracing wire pulling shift fork, replaces traditional halting mechanism.
Gear corresponding on two input shafts of the present invention shares respectively the gear corresponding with it on the output shaft, reduces the number of gears on the output shaft, adopts gear repeatedly to mesh, and effectively reduces the axial length of speed changer, makes speed changer compacter, improves reliability; In the design of reversing gear, do not adopt traditional idler shaft, change sense of rotation and realize reversing gear, improved the efficient of reversing gear, the headspace of gearbox is reduced, be more conducive to the vehicle design.
The present invention adopts dual input shaft to arrange at a certain distance, uses two common clutches, has utilized to greatest extent existing equipment and technology, effectively reduces development cost; Owing to do not adopt concentric shafts, the axial length of speed changer shortens simultaneously, and system stiffness improves.
Description of drawings
Fig. 1 is structural representation of the present invention.
Embodiment
With reference to accompanying drawing embodiments of the invention are discussed in detail.
The actuation gear 1 that present embodiment is positioned on the engine spindle rotates with motor.Drive the master end/slave end of two clutches (first clutch 3 and second clutch 2), the slave end/master end of two clutches connects respectively corresponding input shaft.Two abreast arrangements separated by a distance of input shaft, i.e. the first input shaft 24 and the second input shaft 10.
One gear driving gear 23 of odd number gear driving tooth wheels, three gear driving gears 20, five gear driving gears 19, seven gear driving gear 22 and the driven gears 7 that reverse gear are arranged on the first input shaft 24; Two gear driving gears 6 of even number gear driving tooth wheels, four gear driving gears 4, six gear driving gears 9 and the driving gear 21 that reverses gear are arranged on the second input shaft 10; Five gear driving gears 19 are connected by the first synchronizer 17 with three gear driving gears 20, seven gear driving gears 22 are connected with the second synchronizer 18, four gear driving gears 4 are connected by the 3rd synchronizer 5 with two gear driving gears 6, six gear driving gears 9 are connected by the 4th synchronizer 8 with the driving gear 21 that reverses gear, and the first driven gear 11 of driven tooth wheels, the second driven gear 15, the 3rd driven gear 14 and the 4th driven gear 16 are arranged on the output shaft 13; The first driven gear 11 and a gear driving gear 23 engagements; The second driven gear 15 and two gear driving gears 6,20 engagements of three gear driving gears; The 3rd driven gear 14 and four gear driving gears 4,19 engagements of five gear driving gears; The 4th driven gear 16 and six gear driving gears 9,22 engagements of seven gear driving gears; The driven gear 7 and three that reverses gear keeps off driving gears 20 and connects firmly, reverse gear driven gear 7 and driving gear 21 engagements of reversing gear, and synchronizer 12 is arranged on the output shaft 13, connects the first driven gear 11.
The actuation gear 1 that the present invention is positioned on the engine spindle rotates with motor.Drive the master end/slave end of two clutches (first clutch 3 and second clutch 2), the slave end/master end of two clutches connects respectively corresponding input shaft.Two abreast arrangements separated by a distance of input shaft, i.e. the first input shaft 24 and the second input shaft 10.Joint gear ring 25 parts of halting mechanism and casing connect firmly or be designed to can not be around output shaft rotation, and it cooperates with output shaft synchronous device 12, realizes parking function by gear-shifting bracing wire pulling shift fork.
The power transmission line of each gear is as follows:
1 gear: motor---actuation gear 1---first clutch 3---gear driving gear 23---first driven gear a 11---output shaft 13(power output)
2 gears: motor---actuation gear 1---second clutch 2---two gear driving gear 6---second driven gear 15---output shaft 13(power outputs)
3 gears: motor---actuation gear 1---first clutch 3---three gear driving gear 20---second driven gear 15---output shaft 13(power outputs)
4 gears: motor---actuation gear 1---second clutch 2---four gear driving gear 4---the 3rd driven gear 14---output shaft 13(power outputs)
5 gears: motor---actuation gear 1---first clutch 3 gear driving gear 19---the 3rd driven gear 14---output shafts (13)
6 gears: motor---actuation gear 1---second clutch 2---six gear driving gear 9---the 4th driven gear 16---output shaft 13(power outputs)
7 gears: motor---actuation gear 1---first clutch 3---seven gear driving gear 22---the 4th driven gear 16---output shaft 13(power outputs)
R gear: motor---actuation gear 1---second clutch 2---driving gear 21 reverses gear---and driven gear 7 reverses gear---three gear driving gear 20---second driven gear 15---output shaft 13(power outputs).
Claims (1)
1. axle dual-clutch transmission, it is characterized in that: comprise two clutches, two input shafts, an output shaft, power drives two clutches by motor with gear transmission or with the mode of transmission, two clutches are continuous with corresponding input shaft respectively, and a gear driving gear, three of odd number gear driving tooth wheels keeps off driving gears, five gear driving gears, seven keep off driving gears and the driven gear that reverses gear is arranged on the first input shaft; Two gear driving gears of even number gear driving tooth wheels, four gear driving gears, six gear driving gears and the driving gear that reverses gear are arranged on the second input shaft; Five gear driving gears are connected by the first synchronizer with three gear driving gears, seven gear driving gears are connected with the second synchronizer, four gear driving gears are connected by the 3rd synchronizer with two gear driving gears, six gear driving gears are connected by the 4th synchronizer with the driving gear that reverses gear, and the first driven gear of driven tooth wheels, the second driven gear, the 3rd driven gear and the 4th driven gear are arranged on the output shaft; The first driven gear and a gear driving gear engagement; The second driven gear and two gear driving gears, three gear driving gear engagements; The 3rd driven gear and four gear driving gears, five gear driving gear engagements; The 4th driven gear and six gear driving gears, seven gear driving gear engagements; The driven gear and three that reverses gear keeps off driving gears and connects firmly, reverse gear driven gear and the driving gear engagement of reversing gear, and the output shaft synchronous device connects the first driven gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012105019151A CN102966706A (en) | 2011-03-30 | 2011-03-30 | Three-shaft double-clutch speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012105019151A CN102966706A (en) | 2011-03-30 | 2011-03-30 | Three-shaft double-clutch speed changer |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201110077962 Division CN102182795B (en) | 2011-03-30 | 2011-03-30 | Transmission with three shafts and two clutches |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102966706A true CN102966706A (en) | 2013-03-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012105019151A Pending CN102966706A (en) | 2011-03-30 | 2011-03-30 | Three-shaft double-clutch speed changer |
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| CN (1) | CN102966706A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103256347A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Multi-clutch transmission provided with conflux planetary gear set |
| CN103256351A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Multi-clutch speed variator |
| CN103256346A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Planet row convergence type multi-clutch speed changer |
| CN103758945A (en) * | 2013-12-25 | 2014-04-30 | 浙江吉利控股集团有限公司 | Dual-clutch automatic transmission |
| CN106051071A (en) * | 2015-04-08 | 2016-10-26 | 铃木株式会社 | Automatic transmission |
| CN107830127A (en) * | 2017-11-30 | 2018-03-23 | 江苏沃得农业机械有限公司 | The main speed-changing mechanism of gear box of tractor |
| CN108223780A (en) * | 2018-01-31 | 2018-06-29 | 杭州贵腾汽车传动科技有限公司 | The gear shifting actuating mechanism of DCT double clutch automatic speed changing casees |
| CN109952457A (en) * | 2016-10-21 | 2019-06-28 | 舍弗勒技术股份两合公司 | Double clutch transmission |
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| DE3621545A1 (en) * | 1986-06-27 | 1988-01-28 | Tropp Axel Dipl Ing Fh | Double clutch gear box for vehicles - has gear levels divided between two input shafts selectable by separate clutch units |
| US6050152A (en) * | 1996-03-15 | 2000-04-18 | Ab Volvo | Motor vehicle gearbox |
| CN101052825A (en) * | 2004-09-23 | 2007-10-10 | 安东诺夫汽车技术有限公司 | Double-clutch speed variator for vehicles |
| WO2010071247A1 (en) * | 2008-12-16 | 2010-06-24 | Myung Koo Kang | Multiple-clutch transmission, mct |
| JP2010151159A (en) * | 2008-12-24 | 2010-07-08 | Hitachi Nico Transmission Co Ltd | Twin clutch type transmission for railway motor car |
| CN101776131A (en) * | 2008-12-23 | 2010-07-14 | 格特拉克·福特传动系统有限公司 | Dual-clutch transmission and control the method for this dual-clutch transmission |
| CN101858421A (en) * | 2009-04-03 | 2010-10-13 | 通用汽车环球科技运作公司 | Seven speed dual clutch transmission |
| US20100269613A1 (en) * | 2009-04-24 | 2010-10-28 | Kang Myungkoo | Multi-clutch transmission having dual front-positioned gears and method of operating the same |
| CN201973185U (en) * | 2011-03-30 | 2011-09-14 | 浙江万里扬变速器股份有限公司 | Three-shaft two-clutch transmission |
-
2011
- 2011-03-30 CN CN2012105019151A patent/CN102966706A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3621545A1 (en) * | 1986-06-27 | 1988-01-28 | Tropp Axel Dipl Ing Fh | Double clutch gear box for vehicles - has gear levels divided between two input shafts selectable by separate clutch units |
| US6050152A (en) * | 1996-03-15 | 2000-04-18 | Ab Volvo | Motor vehicle gearbox |
| CN101052825A (en) * | 2004-09-23 | 2007-10-10 | 安东诺夫汽车技术有限公司 | Double-clutch speed variator for vehicles |
| WO2010071247A1 (en) * | 2008-12-16 | 2010-06-24 | Myung Koo Kang | Multiple-clutch transmission, mct |
| CN101776131A (en) * | 2008-12-23 | 2010-07-14 | 格特拉克·福特传动系统有限公司 | Dual-clutch transmission and control the method for this dual-clutch transmission |
| JP2010151159A (en) * | 2008-12-24 | 2010-07-08 | Hitachi Nico Transmission Co Ltd | Twin clutch type transmission for railway motor car |
| CN101858421A (en) * | 2009-04-03 | 2010-10-13 | 通用汽车环球科技运作公司 | Seven speed dual clutch transmission |
| US20100269613A1 (en) * | 2009-04-24 | 2010-10-28 | Kang Myungkoo | Multi-clutch transmission having dual front-positioned gears and method of operating the same |
| CN201973185U (en) * | 2011-03-30 | 2011-09-14 | 浙江万里扬变速器股份有限公司 | Three-shaft two-clutch transmission |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103256351B (en) * | 2013-04-28 | 2015-08-19 | 河南科技大学 | Multi-clutch speed change gear |
| CN103256351A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Multi-clutch speed variator |
| CN103256346A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Planet row convergence type multi-clutch speed changer |
| CN103256347A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Multi-clutch transmission provided with conflux planetary gear set |
| CN103256347B (en) * | 2013-04-28 | 2015-07-15 | 河南科技大学 | Multi-clutch transmission provided with conflux planetary gear set |
| CN103256346B (en) * | 2013-04-28 | 2015-08-19 | 河南科技大学 | Planet row convergent current type multi-clutch speed changer |
| CN103758945A (en) * | 2013-12-25 | 2014-04-30 | 浙江吉利控股集团有限公司 | Dual-clutch automatic transmission |
| CN106051071A (en) * | 2015-04-08 | 2016-10-26 | 铃木株式会社 | Automatic transmission |
| CN106051071B (en) * | 2015-04-08 | 2019-03-19 | 铃木株式会社 | Automatic transmission |
| CN109952457A (en) * | 2016-10-21 | 2019-06-28 | 舍弗勒技术股份两合公司 | Double clutch transmission |
| CN109952457B (en) * | 2016-10-21 | 2021-03-02 | 舍弗勒技术股份两合公司 | Double clutch transmission |
| CN107830127A (en) * | 2017-11-30 | 2018-03-23 | 江苏沃得农业机械有限公司 | The main speed-changing mechanism of gear box of tractor |
| CN108223780A (en) * | 2018-01-31 | 2018-06-29 | 杭州贵腾汽车传动科技有限公司 | The gear shifting actuating mechanism of DCT double clutch automatic speed changing casees |
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| PB01 | Publication | ||
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| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
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Application publication date: 20130313 |