CN104455236A - Double-clutch speed changer transmission device - Google Patents

Double-clutch speed changer transmission device Download PDF

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Publication number
CN104455236A
CN104455236A CN201410707269.3A CN201410707269A CN104455236A CN 104455236 A CN104455236 A CN 104455236A CN 201410707269 A CN201410707269 A CN 201410707269A CN 104455236 A CN104455236 A CN 104455236A
Authority
CN
China
Prior art keywords
gear
output shaft
shaft
output
transmission
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.)
Pending
Application number
CN201410707269.3A
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Chinese (zh)
Inventor
方志勤
尹良杰
祁稳
郑海兵
汪敏
汪文江
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Anhui Jianghuai Automobile Group Corp
Original Assignee
Anhui Jianghuai Automobile Group Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Anhui Jianghuai Automobile Group Corp filed Critical Anhui Jianghuai Automobile Group Corp
Priority to CN201410707269.3A priority Critical patent/CN104455236A/en
Publication of CN104455236A publication Critical patent/CN104455236A/en
Pending legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H37/00Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H57/00General details of gearing
    • F16H57/02Gearboxes; Mounting gearing therein
    • F16H57/023Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly

Abstract

The invention provides a double-clutch speed changer transmission device. The axial length of the double-clutch speed changer transmission device is reduced through an intermediate shaft, three output shafts and gear pairs of all gear positions, and the structure is made more compact.

Description

A kind of transmission device of double clutch transmission
Technical field
The present invention relates to speed changer field.
Background technique
Typical transmission device of double clutch transmission is referred to and is connected by two clutches respectively with two input shafts, transmits engine power.
Double clutch transmissions is by two groups of coaxial nested or clutches of being arranged in parallel, coaxially, two input shafts of inside and outside nested arrangement, two output shafts be arranged in parallel, are arranged in the multiple synchromesh gears on output shaft, multiple reverse shift fork and 1 differential mechanism composition.The odd, even several grades of driving gears of speed changer are arranged on two input shafts, two output shafts are provided with the driven gear engaged with driving gear, by switching and the different synchronizer action of two clutches, realize torque conversion and output via different output shaft.
Existing dual-clutch transmission all adopts inside and outside nested arrangement dual input shaft, be arranged in parallel double output shaft, or increases a reverse gear shaft be arranged in parallel again.For seven grades, interior, outer input shaft needs arrange 1 respectively, 3, 4, 7 and 2, 4, 6, reverse driving gear, two output shafts need to arrange 1 respectively, 3, 4, 7 and 2, 4, 6, reverse gear driven gear, although utilize synchronizer that single gear can be made to possess multiple gear torque output function in prior art, reduce the axial length of transmission assembly to a certain extent, in any case but, increasing of gear number must bring the axial length of transmission assembly to increase, this arranges it is disadvantageous for gearbox, especially when input torque is larger, axial length is not easy to control more, the compactedness requirement that passenger car is more and more higher can not be adapted to, reduce arrangement flexibility, especially the layout of front horizontal forerunner's passenger car is unfavorable for.
Summary of the invention
Object of the present invention overcomes the long problem of dual-clutch transmission axial length of many gears, provides the transmission device of double clutch transmission that a kind of structure is compacter, be easier to control, The embodiment provides following technological scheme for this reason:
A kind of transmission device of double clutch transmission, comprising: first clutch and second clutch, coaxially nested interior input shaft and outer input shaft, described interior input shaft is connected with described first clutch, and described outer input shaft is connected with described second clutch, and described interior input shaft and described outer input shaft are provided with multiple different gear driving gear, the first output shaft be arranged in parallel with described interior input shaft and described outer input shaft and the second output shaft, described first output shaft and described second output shaft are provided with the multiple driven gear engaged with described driving gear respectively and optionally by transmission of power to the synchronizer of described driven gear, differential mechanism, described first output shaft and described second output shaft have the first output shaft output gear and the second output shaft output gear that engage with the final gear of described differential mechanism respectively, also comprise the jack shaft and the 3rd output shaft that be arranged in parallel with described interior input shaft and described outer input shaft, described jack shaft has intermediate gear and multiple input gear, described intermediate gear engages with a driven gear on described second output shaft, described 3rd output shaft have the multiple driven gears engaged with described input gear, described 3rd output shaft or described jack shaft are provided with optionally by transmission of power to the synchronizer of the driven gear on described 3rd output shaft, described 3rd output shaft also has the 3rd output shaft output gear engaged with the final gear of described differential mechanism.
Preferably, described first output shaft output gear and described second output shaft output gear are separately positioned on the low order end of described first output shaft and described second output shaft, and described 3rd output shaft output gear is arranged on the high order end of described 3rd output shaft.
Preferably, described second output shaft is provided with duplicate gear, a gear in described duplicate gear is as the driven gear engaged with the intermediate gear on described jack shaft, and another gear is as the idle pulley that reverses gear engaged with the driven gear that reverses gear on described first output shaft.
The present invention adopts the intermediate gear of jack shaft to engage with a driven gear of the second output shaft, by multiple input gear transmission of power given the multiple driven gears on the 3rd output shaft again, like this, just a moment of torsion of the driven gear of on the second output shaft is exported the multiple moments of torsion be converted on the 3rd output shaft to export, this just means under the condition of identical gear number, the axial length of whole transmission device of double clutch transmission can shorten further, more gear can be arranged on three output shafts in other words under the condition not increasing axial length, make structure compacter, be easy to control, the passenger car being particularly suitable for front horizontal forerunner is arranged, especially it is sometimes more obvious when Engine torque reaches the high pulling torque of more than 300Nm.
Further, after adopting duplicate gear, the driven gear engaged with intermediate gear is used as reverse idler gear simultaneously, eliminate reverse gear shaft and extra reverse idler gear, decrease amount of parts, decrease gear box casing processing, Detection of content, decrease double clutch general assembly step, reduce cost.
Further, the arrangement of three output gears and the existence of jack shaft, enable park pawl be arranged on the left of intermediate gear or on the left of the 3rd output shaft output gear, for park pawl provides enough spaces, improve higher space placement of flexible.
Accompanying drawing explanation
Next will be described in further detail specific embodiments of the invention by reference to the accompanying drawings, wherein:
Fig. 1 is the transmission device of double clutch transmission structural representation of embodiments of the invention.
Description of symbols in upper figure: interior input shaft 1, outer input shaft 2, first output shaft 3, second output shaft 4, jack shaft 5, 3rd output shaft 6, differential mechanism 7, one grade of driving gear 11, seven grades of driving gears 17, third speed drive gear 13, second gear driving gear 22, first speed driven gear 31, third gear driven gear 33, reverse gear driven gear 34, first output shaft output gear 30, seven grades of driven gears 47, five grades of driven gears 45, second gear driven gear 42, reverse idler gear 43, second output shaft output gear 40, intermediate gear 50, fourth gear input gear 54, six grades of input gears 56, fourth gear driven gear 64, six grades of driven gears 66, 3rd output shaft output gear 60, final gear 70, first synchronizer SC1, second synchronizer SC2, 3rd synchronizer SC3, 4th synchronizer SC4, 5th synchronizer SC5, first clutch C1, second clutch C2.
Embodiment
In next described embodiment, transmission device of double clutch transmission has seven forward gear one reverse gears, but this can not be considered to the restriction to gear number of the present invention, those skilled in the art can increase gear number or reduce as required.
With reference to figure 1, in transmission device of double clutch transmission, interior input shaft 1 is coaxially nested with outer input shaft 2, and interior input shaft 1 can rotate by external input shaft 2 mutually.Interior input shaft 1 is connected with first clutch C1, and outer input shaft 2 is connected with second clutch C2, by the open and close controlling of clutch C1 and C2, Engine torque can be delivered to interior input shaft 1 or outer input shaft 2 selectively.In Fig. 1 with away from motor side be left, near motor side for the right side, interior input shaft 1 is arranged from left to right successively one grade of driving gear, 11, seven grades of driving gears 17 and third speed drive gear 13, wherein, third speed drive gear 13 is also used by as five grades of driving gears simultaneously; Outer input shaft 2 only arranges second gear driving gear 22, and wherein, second gear driving gear is used by as reverse driving gear simultaneously.Like this, from whole input shaft assembly 1,2, odd number shelves are disposed on interior input shaft 1, even number shelves are disposed on outer input shaft 2, and arrangement of gears order is followed successively by from left to right: one grade of driving gear 11, seven grades of driving gears 17, three (five) shelves driving gear 13, two (falling) shelves driving gear 22.Certainly, the distributing order of these driving gears also can change as required.
To be arranged in parallel the first output shaft 3, second output shaft 4, jack shaft 5 and the 3rd output shaft 6 with interior input shaft 1 and outer input shaft 2.
On the first output shaft 3, be provided with first speed driven gear 31, third gear driven gear 33, reverse gear driven gear 34 from left to right, they often engage with a grade on inside and outside input shaft 1,2, third gear, reverse driving gear respectively, constitute one, three, reverse gear; Reverse gear driven gear on reverse gear driven gear 34 and the second output shaft 4 43 (be duplex-gear structure with second gear driven tooth 42) often engages, and together form reverse gear with second gear driving gear 22 on interior input shaft 2.Above driven gear all by bearings on the first output shaft 3, namely above driven gear can to rotate relative to the first output shaft 3 on the first output shaft 3.The first synchronizer SC1 is arranged between first speed driven gear 31 and third gear driven gear 33, the second synchronizer SC2 is arranged between reverse gear driven gear 34 and third gear driven gear 33, first synchronizer SC1 and the second synchronizer SC2 is rigidly connected by spline or alternate manner and the first output shaft 3, namely can by the first synchronizer SC1 and the second synchronizer SC2 by transmission of power to the first output shaft 3.Like this, be optionally connected on one, three or reverse gear driven gear by the first synchronizer SC1 and the second synchronizer SC2, just can realize transmission of power to the first output shaft 3.The first output shaft output gear 30 (or claiming the first output shaft main deceleration driving gear) is also provided with at the low order end (near engine side) of the first output shaft, it and differential mechanism final gear 70 often engage, and the first output shaft 3 moment of torsion is delivered to differential mechanism 7.
On second output shaft 4, (away from motor side for left, close motor side is for right) is provided with seven grades of driven gears, 47, five grades of driven gears 45, second gear driven gear 42 (second gear driven gear 42 and reverse gear driven gear 43 are duplex-gear structure) from left to right, they often engage with reverse gear driven gear 34 on seven grades of driving gear 17, three (five) shelves driving gears 13, second gear driving gear 22 and first output shafts 3 on input shaft respectively, constitute seven grades, five grades, second gear and reverse gear.Above driven gear all by bearings on the second output shaft 4, namely above driven gear can to rotate relative to the second output shaft 4 on the second output shaft 4.The 3rd synchronizer SC3 is arranged between seven grades of driven gears 47 and five grades of driven gears 45, the 4th synchronizer SC4 is arranged between second gear driven gear 42 and five grades of driven gears 45,3rd synchronizer SC3 and the 4th synchronizer SC4 is rigidly connected by spline or alternate manner and the second output shaft 4, namely can by the 3rd synchronizer SC3 and the 4th synchronizer SC4 by transmission of power to the second output shaft 4.Like this, the 3rd synchronizer SC3 and the 4th synchronizer SC4 is optionally connected to seven, five, on second gear driven gear, just can realize by transmission of power to the second output shaft 4, and finally be delivered to differential mechanism 7.The second output shaft output gear 40 (or claiming the second output shaft main deceleration driving gear) is provided with at the low order end (near engine side) of the second output shaft 4, it and differential mechanism final gear 70 often engage, and the second output shaft 4 moment of torsion is delivered to differential mechanism 7.
On jack shaft 5, (away from motor side for left, close motor side is for right) is provided with intermediate gear 50, six grades of input gears 56 and fourth gear input gear 54 from left to right.Wherein intermediate gear 50 often engages with the second gear driven tooth 42 on the second output shaft 4, and meanwhile, intermediate gear 50 and jack shaft 5 are for being fixedly connected with, and namely intermediate gear 50 can by transmission of power to jack shaft 5.
On 3rd output shaft 6, (away from motor side for left, close motor side is for right) is provided with the 3rd output shaft output gear 60, six grades of driven gears 66 and fourth gear driven gear 64 from left to right.Between six grades of driven gears 66 and fourth gear driven gear 64, arrange the 5th synchronizer SC5, the 5th synchronizer SC5 is rigidly connected by spline or alternate manner and the 3rd output shaft 6, namely can by the 5th synchronizer SC5 by transmission of power to the 3rd output shaft 6.3rd output shaft output gear 60 often engages with differential mechanism final gear 70, and the 3rd output shaft 6 moment of torsion is delivered to differential mechanism 7.
Power transmission line illustrates:
One grade of power transmission line: the first synchronizer SC1 and first speed driven gear 31 combine, first clutch C1 closes, Engine torque passes to interior input shaft 1 by first clutch C1, often driving gear 11, driven gear 31 and the first synchronizer SC1 is engaged via one grade, transfer torque to the first output shaft 3, by the first output shaft output gear 30 and differential mechanism final gear 70, moment of torsion is passed to differential mechanism 7 again, and final by differential mechanism 7 outputting power.
Second gear power transmission line: the 4th synchronizer SC4 and second gear driven gear 42 combine, second clutch C2 closes, Engine torque passes to outer input shaft 2 by second clutch C2, driving gear 22, driven gear 42 and the 3rd synchronizer SC3 is often engaged via second gear, transfer torque to the second output shaft 4, by the second output shaft output gear 40 and differential mechanism final gear 70, moment of torsion is passed to differential mechanism 7 again, and final by differential mechanism 7 outputting power.
Third gear power transmission line: the first synchronizer SC1 and third gear driven gear 33 combine, first clutch C1 closes, Engine torque passes to interior input shaft 1 by first clutch C1, driving gear 13, driven gear 33 and the first synchronizer SC1 is often engaged via third gear, transfer torque to the first output shaft 3, by the first output shaft output gear 30 and differential mechanism final gear 70, moment of torsion is passed to differential mechanism 7 again, and final by differential mechanism 7 outputting power.
Fourth gear power transmission line: the 5th synchronizer SC5 and fourth gear driven gear 64 combine, second clutch C2 closes, Engine torque passes to outer input shaft 2 by second clutch C2, driving gear 22, driven gear 42 and intermediate gear 50, jack shaft 5, fourth gear input gear 54 is often engaged via second gear, transfer torque to the 3rd output shaft 6, by the 3rd output shaft output gear 60 and differential mechanism final gear 70, moment of torsion is passed to differential mechanism 7 again, and final by differential mechanism 7 outputting power.
Five grades of power transmission lines: the 3rd synchronizer SC3 and five grade driven gear 45 combines, first clutch C1 closes, Engine torque passes to interior input shaft 1 by first clutch C1, often driving gear 13, driven gear 45 and the 4th synchronizer SC4 is engaged via five grades, transfer torque to the second output shaft 4, by the second output shaft output gear 40 and differential mechanism final gear 70, moment of torsion is passed to differential mechanism 7 again, and final by differential mechanism 7 outputting power.
Six grades of power transmission lines: the 5th synchronizer SC5 and six grade driven gear 66 combines, second clutch C2 closes, Engine torque passes to outer input shaft 2 by second clutch C2, driving gear 22, driven gear 42 and center tooth 50, jack shaft 5, six grades of input gears 56 are often engaged via second gear, transfer torque to the 3rd output shaft 6, by the 3rd output shaft output gear 60 and differential mechanism final gear 70, moment of torsion is passed to differential mechanism 7 again, and final by differential mechanism 7 outputting power.
Reverse gear transfer route: the second synchronizer SC2 and reverse gear driven gear 34 combine, second clutch C2 closes, Engine torque passes to outer input shaft 2 by clutch C2, driving gear 22, second gear driven gear 42 (simultaneously as reverse gear intermediate idler to change pinion rotation direction), reverse gear driven gear 43, reverse gear driven gear 34, second synchronizer SC2 is often engaged through second gear, first output shaft 3, by the first output shaft output gear 30 and differential mechanism final gear 70, moment of torsion is passed to differential mechanism 7 again, and final by differential mechanism 7 outputting power.
Gearshift procedure illustrates:
One grade is changed second gear process: dual-clutch transmission is in one grade, and the first synchronizer SC1 and first speed driven gear 31 combine, and first clutch C1 closes, and second clutch C2 opens; Dual-clutch transmission control system (not showing in accompanying drawing 1) sends one grade and changes second gear instruction, 4th synchronizer SC4 and second gear driven gear 42 combine by gear-shifting actuating mechanism in advance, now second clutch C2 is still in open mode, i.e. second clutch C2 and the second output shaft 4 not transferring power; Along with gearshift procedure continues, first clutch C1 opens gradually, and meanwhile, second clutch C2 closes gradually, and this process there will not be torque break; First clutch C1 opens completely, second clutch C2 completely closed after, first synchronizer SC1 throws off the combination with first speed driven gear 31, terminate gearshift procedure, Engine torque is via second clutch C2, outer input shaft 2, second gear driving gear 22, second gear driven gear 42, the 3rd synchronizer SC3, the second output shaft 4, second output shaft output gear 40, differential mechanism final gear 70, finally exported by differential mechanism 7.
Visible by foregoing description, the present embodiment adopts the intermediate gear 50 of jack shaft 5 to engage with a driven gear 42 of the second output shaft 4, the multiple driven gears on the 3rd output shaft 6 are given by transmission of power again by six grades of input input gears 56 and fourth gear input gear 54, like this, just a moment of torsion of a driven gear on the second output shaft 4 is exported the multiple moments of torsion be converted on the 3rd output shaft 6 to export, this just means under the condition of identical gear number, the axial length (length on left and right directions) of whole transmission device of double clutch transmission can shorten further, more gear can be arranged on three output shafts in other words under the condition not increasing axial length, make structure compacter, be easy to control, the passenger car being particularly suitable for front horizontal forerunner is arranged, especially it is sometimes more obvious when Engine torque reaches the high pulling torque of more than 300Nm.And after adopting duplicate gear 42,43, the driven gear engaged with intermediate gear 50 is used as reverse idler gear simultaneously, eliminate reverse gear shaft and extra reverse idler gear, decrease amount of parts, decrease gear box casing processing, Detection of content, decrease double clutch general assembly step, reduce cost.And the existence of the arrangement of three output gears and jack shaft 5, enables park pawl be arranged on the left of intermediate gear 50 or on the left of the 3rd output shaft output gear 60, for park pawl provides enough spaces, improves higher space placement of flexible.
Although the present invention is described in conjunction with above embodiment, but the present invention is not limited to above-described embodiment, and only by the restriction of claims, those of ordinary skill in the art can easily modify to it and change, but do not leave essential idea of the present invention and scope.

Claims (3)

1. a transmission device of double clutch transmission, is characterized in that, comprising:
First clutch and second clutch;
Coaxially nested interior input shaft and outer input shaft, described interior input shaft is connected with described first clutch, and described outer input shaft is connected with described second clutch, and described interior input shaft and described outer input shaft are provided with multiple different gear driving gear;
The first output shaft be arranged in parallel with described interior input shaft and described outer input shaft and the second output shaft, described first output shaft and described second output shaft are provided with the multiple driven gear engaged with described driving gear respectively and optionally by transmission of power to the synchronizer of described driven gear;
Differential mechanism, described first output shaft and described second output shaft have the first output shaft output gear and the second output shaft output gear that engage with the final gear of described differential mechanism respectively;
Also comprise the jack shaft and the 3rd output shaft that be arranged in parallel with described interior input shaft and described outer input shaft, described jack shaft has intermediate gear and multiple input gear, described intermediate gear engages with a driven gear on described second output shaft, described 3rd output shaft have the multiple driven gears engaged with described input gear, described 3rd output shaft or described jack shaft are provided with optionally by transmission of power to the synchronizer of the driven gear on described 3rd output shaft, described 3rd output shaft also has the 3rd output shaft output gear engaged with the final gear of described differential mechanism.
2. transmission device of double clutch transmission according to claim 1, it is characterized in that, described first output shaft output gear and described second output shaft output gear are separately positioned on the low order end of described first output shaft and described second output shaft, and described 3rd output shaft output gear is arranged on the high order end of described 3rd output shaft.
3. transmission device of double clutch transmission according to claim 1, it is characterized in that, described second output shaft is provided with duplicate gear, a gear in described duplicate gear is as the driven gear engaged with the intermediate gear on described jack shaft, and another gear is as the idle pulley that reverses gear engaged with the driven gear that reverses gear on described first output shaft.
CN201410707269.3A 2014-11-28 2014-11-28 Double-clutch speed changer transmission device Pending CN104455236A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201410707269.3A CN104455236A (en) 2014-11-28 2014-11-28 Double-clutch speed changer transmission device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201410707269.3A CN104455236A (en) 2014-11-28 2014-11-28 Double-clutch speed changer transmission device

Publications (1)

Publication Number Publication Date
CN104455236A true CN104455236A (en) 2015-03-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN201410707269.3A Pending CN104455236A (en) 2014-11-28 2014-11-28 Double-clutch speed changer transmission device

Country Status (1)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108016277A (en) * 2016-10-31 2018-05-11 比亚迪股份有限公司 Power drive system and there is its vehicle
CN113389854A (en) * 2020-03-11 2021-09-14 广州汽车集团股份有限公司 Eight-speed double-clutch transmission and automobile

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108016277A (en) * 2016-10-31 2018-05-11 比亚迪股份有限公司 Power drive system and there is its vehicle
US10974591B2 (en) 2016-10-31 2021-04-13 Byd Company Limited Power transmission system and vehicle having same
CN113389854A (en) * 2020-03-11 2021-09-14 广州汽车集团股份有限公司 Eight-speed double-clutch transmission and automobile
CN113389854B (en) * 2020-03-11 2022-04-12 广州汽车集团股份有限公司 Eight-speed double-clutch transmission and automobile

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Address after: 230601 Anhui Province, Hefei City Industrial Park, the Peach Blossom Road No. 669

Applicant after: Anhui Jianghuai Automobile Group Limited by Share Ltd

Address before: 230601 Anhui Province, Hefei City Industrial Park, the Peach Blossom Road No. 669

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Application publication date: 20150325

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