CN202914643U - Transmission device of double-clutch speed changer - Google Patents
Transmission device of double-clutch speed changer Download PDFInfo
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- CN202914643U CN202914643U CN 201220552439 CN201220552439U CN202914643U CN 202914643 U CN202914643 U CN 202914643U CN 201220552439 CN201220552439 CN 201220552439 CN 201220552439 U CN201220552439 U CN 201220552439U CN 202914643 U CN202914643 U CN 202914643U
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Abstract
The utility model relates to a transmission device of a double-clutch speed changer. The device comprises an inner input shaft, an outer input shaft, a first output shaft, a second output shaft, gears, two clutches and four synchronizers, wherein the inner input shaft and the outer input shaft are arranged coaxially, the gears are arranged on all shafts, a fifth gear driving gear on the inner input shaft is used as a seventh gear driving gear at the same time, a fourth gear driving gear on the outer input shaft is used as a sixth gear driving gear at the same time, a second gear driving gear is used as a reverse gear driving gear, a first synchronizer transmits a first gear torsion and a fifth gear torsion to the first output shaft selectively, a second synchronizer transmits a fourth gear torsion and a reverse gear torsion to the first output shaft selectively, a third synchronizer transmits a seventh gear torsion and a third gear torsion to the second output shaft selectively, and a fourth synchronizer transmits a sixth gear torsion and a second gear torsion to the second output shaft selectively. According to the transmission device of the double-clutch speed changer, the axial length of the speed changer is decreased, and arrangement of all gears of gears is enabled to be well matched with the center distance of the speed changer.
Description
Technical field
The utility model belongs to the automotive transmission technical field, is specifically related to transmission device of double clutch transmission.
Background technique
To the intermediate shaft type speed changer, the distance between jack shaft and the second axle is speed changer centre distance, and not only to the boundary dimension of speed changer, volume and quality are big or small, and influential to the contact strength of the gear teeth for its size.Centre distance is less, and the contact stress of gear is large, and gear life is short.The minimum centre distance that allows is determined when the contact strength that guaranteed gear is necessary.Transmission shaft is installed on the housing through bearing, from arranging may considering with convenient intensity with not affecting housing of bearing, requires centre distance to get greatly.Be subjected in addition the restriction that one grade of small gear number of teeth can not be very few, require centre distance also to want large.Generally, when carrying out transmission design, need to distribute each grade gear number of teeth through after the primary election centre distance according to speed changer gear number, velocity ratio and transmission scheme, again centre distance is revised, redistribute each grade gear number of teeth.
Typical transmission device of double clutch transmission refer to by two clutches respectively with are connected an input shaft and connect, transmit engine power.Double clutch transmissions is by two groups of coaxial nested or clutches of being arranged in parallel, two input shafts of coaxial, inside and outside nested arrangement, two output shafts that are arranged in parallel are arranged in a plurality of synchronizers on the output shaft, a plurality of reverse shift fork and 1 differential mechanism and form.Speed changer is strange, even number shelves input gear is arranged on two input shafts, and switching and the action of different synchronizer by two clutches realize torque conversion and output via different output shafts.Owing to have two input shafts, two output shafts, so that the relation that centre distance and gear distribute is more complicated, the matching between centre distance and each grade arrangement of gears can produce material impact to transmission performance.Be in the application for a patent for invention of CN 102252063A at application publication number, the applicant discloses a kind of double-clutch automatic gearbox transmission device, short, the less advantage of part of axial length with speed changer, but find in practice, in the disclosed technological scheme, the matching of speed changer centre distance and each grade arrangement of gears is not fine, affects gear life.
The model utility content
The problem of mating in order to solve centre distance that existing dual-clutch transmission exists and each grade arrangement of gears, the utility model provides a kind of new structure transmission device of double clutch transmission.
The utility model realizes that the technical solution of above-mentioned purpose is as follows:
A kind of transmission device of double clutch transmission comprises:
The interior input shaft I1 of coaxial setting and outer input shaft I2, described outer input shaft I2 is hollow shaft, is nested on the described interior input shaft I1;
The first output shaft TW1 and the second output shaft TW2;
First clutch C1 and second clutch C2, described first clutch C1 is located at the end of described interior input shaft I1, and described second clutch C2 is located at described outer input shaft I2 one end; It is characterized in that:
Be fixed with successively one grade of driving gear 1, third speed drive gear 2 and five grades of driving gears 3 on the other end of described interior input shaft I1, described 3 whiles of five grades of driving gears are as seven grades of driving gears;
Be fixed with successively fourth gear driving gear 4 and second gear driving gear 5 on the other end of described outer input shaft I2, described 4 whiles of fourth gear driving gear, described 5 whiles of second gear driving gear were as reverse driving gear as six grades of driving gears;
Be provided with successively first speed driven gear 6, five grades of driven gears 7, fourth gear driven gear 8, reverse gear driven gear 9 and first output gears 15 on described the first output shaft TW1, wherein said first speed driven gear 6, five grades of driven gears 7, fourth gear driven gear 8, reverse gear driven gear 9 empty sets and can be rotated around described the first output shaft TW1 on described the first output shaft TW1; Described the first output gear 15 is fixedly connected with described the first output shaft TW1, is used for exporting the moment of torsion of the first output shaft TW1; Be fixed with the first synchronizer S1 on described the first output shaft TW1 between described first speed driven gear 6 and the five grades of driven gears 7, optionally first grade of moment of torsion and the 5th grade of moment of torsion passed to the first output shaft TW1; Be fixed with the second synchronizer S2 on described the first output shaft TW1 between described fourth gear driven gear 8 and the reverse gear driven gear 9, optionally fourth speed moment of torsion and reverse gear moment of torsion passed to the first output shaft TW1;
Be provided with successively third gear driven gear 10, seven grades of driven gears 11, six grades of driven gears 12, second gear driven gear 13 and second output gears 14 on described the second output shaft TW2, wherein said third gear driven gear 10, seven grades of driven gears 11, six grades of driven gears 12 and second gear driven gear 13 empty sets and can be rotated around the second output shaft TW2 on described the second output shaft TW2; Described the second output gear 14 is fixedly connected with described the second output shaft TW2, is used for exporting the moment of torsion of described the second output shaft TW2; Be fixed with the 3rd synchronizer S3 on described the second output shaft TW2 between described third gear driven gear 10 and the seven grades of driven gears 11, optionally third gear moment of torsion and the 7th grade of moment of torsion passed to described the second output shaft TW2; Be fixed with the 4th synchronizer S4 on described the second output shaft TW2 between described six grades of driven gears 12 and the second gear driven gear 13, optionally the 6th grade of moment of torsion and second gear moment of torsion passed to described the second output shaft TW2;
Described one grade of driving gear 1 is normal engagement with described first speed driven gear 6, described third speed drive gear 2 is normal engagement with described third gear driven gear 10, described five grades of driving gears 3 are normal engagement with described five grades of driven gears 7, seven grades of driven gears 11 simultaneously, described fourth gear driving gear 4 is normal engagement with described fourth gear driven gear 8, six grades of driven gears 12 simultaneously, described second gear driving gear 5 and described second gear driven gear 13 are normal engagement, and described second gear driven gear 13 and described reverse gear driven gear 9 are normal engagement.
Selectively, also be provided with parking ratchet wheel 17 on described the first output shaft TW1 or described the second output shaft TW2 or the described differential mechanism D.
Useful technique effect of the present utility model embodies in the following areas:
Because the utility model shares five grades of driving gears as five grades and seven grades, rather than third speed drive gear is shared as third gear and five grades, again each grade gear is arranged that the matching of new each grade arrangement of gears and centre distance is better.
Further, parking ratchet wheel is arranged on the first output shaft or the second output shaft or the described differential mechanism, so that structure has more flexibility.
Description of drawings
Fig. 1 is the transmission device of double clutch transmission structural representation of present embodiment;
Fig. 2 is the right elevation of Fig. 1.
Mark among the upper figure: T-transmission device of double clutch transmission, the C1-first clutch, the C2-second clutch, input shaft in the I1-, the outer input shaft of I2-, TW1-the first output shaft, TW2-the second output shaft, the D-differential mechanism, one grade of driving gear of 1-, the 2-third speed drive gear, five grades of driving gears of 3-, 4-fourth gear driving gear, 5-second gear driving gear, the 6-first speed driven gear, five grades of driven gears of 7-, 8-fourth gear driven gear, 9-reverse gear driven gear, 10-third gear driven gear, seven grades of driven gears of 11-, six grades of driven gears of 12-, 13-second gear driven gear, 14-the second output gear, 15-the first output gear, the 16-final gear, S1-the first synchronizer, S2-the second synchronizer, S3-the 3rd synchronizer, S4-the 4th synchronizer.
Embodiment
Below in conjunction with accompanying drawing, by embodiment the utility model is done to describe further.
Referring to Fig. 1 and Fig. 2, transmission device of double clutch transmission T comprises interior input shaft I1 and outer input shaft I2, the first output shaft TW1, the second output shaft TW2, first clutch C1 and the second clutch C2 of coaxial setting; Outer input shaft I2 is hollow shaft, is nested on the interior input shaft I1, and coaxial with interior input shaft I1; First clutch C1 and second clutch C2, first clutch C1 are located at the end of interior input shaft I1, and second clutch C2 is located at outer input shaft I2 one end; Be installed with successively one grade of driving gear 1, third speed drive gear 2 and 3, five grades of driving gears of five grades of driving gears on the other end of interior input shaft I1 simultaneously as seven grades of driving gears.Be installed with successively fourth gear driving gear 4 and second gear driving gear 5 on the other end of outer input shaft I2, the fourth gear driving gear is simultaneously as six grades of driving gears, and the second gear driving gear is simultaneously as reverse driving gear.Be provided with successively first speed driven gear 6, five grades of driven gears 7, fourth gear driven gear 8, reverse gear driven gear 9 and first output gears 15 on the first output shaft TW1; Wherein first speed driven gear 6, five grades of driven gears 7, fourth gear driven gear 8, reverse gear driven gear 9 empty sets are on the first output shaft TW1, and can rotate around the first output shaft TW1; The first output gear 15 is fixedly connected with the first output shaft TW1, is used for exporting the moment of torsion of the first output shaft TW1; Be installed with the first synchronizer S1 on the first output shaft between first speed driven gear 6 and the five grades of driven gears 7, optionally first grade of moment of torsion and the 5th grade of moment of torsion passed to the first output shaft TW1; Be installed with the second synchronizer S2 on the first output shaft TW1 between fourth gear driven gear 8 and the reverse gear driven gear 9, optionally the 5th grade of moment of torsion and reverse gear moment of torsion passed to the first output shaft TW1.Be provided with successively third gear driven gear 10, seven grades of driven gears 11, six grades of driven gears 12, second gear driven gear 13 and second output gears 14 on the second output shaft TW2, wherein third gear driven gear 10, seven grades of driven gears 11, six grades of driven gears 12 and second gear driven gear 13 empty sets are on the second output shaft TW2, and can rotate around the second output shaft TW2.The second output gear 14 is fixedly connected with the second output shaft TW2, is used for exporting the moment of torsion of the second output shaft TW2.Be installed with the 3rd synchronizer S3 on the second output shaft TW2 between third gear driven gear 10 and the seven grades of driven gears 11, the 3rd synchronizer S3 optionally passes to the second output shaft TW2 with third gear moment of torsion and the 7th grade of moment of torsion.Be installed with the 4th synchronizer S4 on the second output shaft TW2 between six grades of driven gears 12 and the second gear driven gear 13, optionally the 6th grade of moment of torsion and second gear moment of torsion passed to the second output shaft TW2.As can be seen from Fig. 1, in the left side of third gear driven gear 10, also be provided with parking ratchet wheel 17 on the second output shaft TW2, parking ratchet wheel 17 is fixedly connected with the second output shaft TW2, to realize parking function.Those of ordinary skills can imagine that parking ratchet wheel 17 can be arranged on the first output shaft TW1 or the differential mechanism D equally as required.
As seen from Figure 1, one grade of driving gear 1 is normal engagement with first speed driven gear 6, third speed drive gear 2 is normal engagement with third gear driven gear 10, five grades of driving gears 3 are normal engagement with five grades of driven gears 7, seven grades of driven gears 11 simultaneously, fourth gear driving gear 4 is normal engagement with fourth gear driven gear 8, six grades of driven gears 12 simultaneously, and second gear driving gear 5 and second gear driven gear 13 are normal engagement.As seen from Figure 2, second gear driven gear 13 and reverse gear driven gear 9 are normal engagement.
Seven forward gearss of this device and the power transmission line of a reverse gear are as follows:
One grade of power transmission line: the first synchronizer S1 and first speed driven gear 6 combinations, first clutch C1 is closed, Engine torque passes to interior input shaft I1 by first clutch C1, via one grade of driving gear 1 of normal engagement and first speed driven gear 6, the first synchronizer S1, transfer torque to the first output shaft TW1, by the first output gear 15 and final gear 16 engagements moment of torsion is passed to differential mechanism D again, and finally by differential mechanism D outputting power.
Second gear power transmission line: the 4th synchronizer S4 and 13 combinations of second gear driven gear, second clutch C2 is closed, Engine torque passes to outer input shaft I2 by second clutch C2, via the second gear driving gear 5 of normal engagement and second gear driven gear 13, the 4th synchronizer S4, transfer torque to the second output shaft TW2, by the second output gear 14 and final gear 16 engagements moment of torsion is passed to differential mechanism D again, and finally by differential mechanism D outputting power.
Third gear power transmission line: the 3rd synchronizer S3 and 10 combinations of third gear driven gear, first clutch C1 is closed, Engine torque passes to interior input shaft I1 by first clutch C1, via the third speed drive gear 2 of normal engagement and third gear driven gear 10, the 3rd synchronizer S3, transfer torque to the second output shaft TW2, by the second output gear 14 and final gear 16 engagements moment of torsion is passed to differential mechanism D again, and finally by differential mechanism D outputting power.
Fourth gear power transmission line: the second synchronizer S2 and 8 combinations of fourth gear driven gear, second clutch C2 is closed, Engine torque passes to outer input shaft I2 by second clutch C2, via the fourth gear driving gear 4 of normal engagement and fourth gear driven gear 8, the second synchronizer S2, transfer torque to the first output shaft TW1, by the first output gear 15 and final gear 16 engagements moment of torsion is passed to differential mechanism D again, and finally by differential mechanism D outputting power.
Five grades of power transmission lines: the first synchronizer S1 and five grades of driven gear 7 combinations, first clutch C1 is closed, Engine torque passes to interior input shaft I1 by first clutch C1, via five grades of driving gears 3 of normal engagement and five grades of driven gears 7, the first synchronizer S1, transfer torque to the first output shaft TW1, by the first output gear 15 and final gear 16 engagements moment of torsion is passed to differential mechanism D again, and finally by differential mechanism D outputting power.
Six grades of power transmission lines: the 4th synchronizer S4 and six grades of driven gear 12 combinations, second clutch C2 is closed, Engine torque passes to outer input shaft I2 by second clutch C2, via six grades of driving gears of normal engagement and six grades of driven gears 12, the 4th synchronizer S4, transfer torque to the second output shaft TW2, by the second output gear 14 and final gear 16 engagements moment of torsion is passed to differential mechanism D again, and finally by differential mechanism D outputting power.
Seven grades of power transmission lines: the 3rd synchronizer S3 and seven grades of driven gear 11 combinations, first clutch C1 is closed, Engine torque passes to interior input shaft I1 by first clutch C1, via seven grades of driving gears of normal engagement and seven grades of driven gears 11, the 3rd synchronizer S3, transfer torque to the second output shaft TW2, by the second output gear 14 and final gear 16 engagements moment of torsion is passed to differential mechanism D again, and finally by differential mechanism D outputting power.
Reverse gear transfer route: the second synchronizer S2 and 9 combinations of reverse gear driven gear, second clutch C2 is closed, Engine torque passes to outer input shaft I2 by second clutch C2, change the gear sense of rotation as idle pulley in the middle of the reverse gear simultaneously through second gear driving gear 5, second gear driven gear 13(), reverse gear driven gear 9, the second synchronizer S2, transfer torque to the first output shaft TW1, by the first output gear 15 and final gear 16 engagements moment of torsion is passed to differential mechanism D again, and finally by differential mechanism D outputting power.
Gearshift procedure illustrates:
One grade is changed the second gear process: dual-clutch transmission is in one grade, the first synchronizer S1 and first speed driven gear 6 combinations, and first clutch C1 is closed, and second clutch C2 opens; Dual-clutch transmission control system (not showing in the accompanying drawing 1) is sent one grade and is changed the second gear instruction, gear-shifting actuating mechanism is in advance with the 4th synchronizer S4 and 13 combinations of second gear driven gear, this moment, second clutch C2 still was in open mode, i.e. second clutch C2 and the second output shaft TW2 transferring power not; Along with gearshift procedure continues, first clutch C1 opens gradually, and meanwhile, second clutch C2 is closed gradually, and this process torque break can not occur; First clutch C1 opens fully, after the complete closure of second clutch C2, the first synchronizer S1 throws off the combination with first speed driven gear 6, finish gearshift procedure, Engine torque is via second clutch C2, outer input shaft I2, second gear driving gear 5, second gear driven gear 13, the 4th synchronizer S4, the second output shaft TW2, the second output gear 14, final gear 16, finally exported by differential mechanism D.
Although the utility model is described in conjunction with above embodiment, but the utility model is not limited to above-described embodiment, and only be subjected to the restriction of claim, those of ordinary skills can easily make amendment to it and change, but do not leave essence design of the present utility model and scope.
Claims (2)
1. transmission device of double clutch transmission comprises:
The interior input shaft (I1) of coaxial setting and outer input shaft (I2), described outer input shaft (I2) is hollow shaft, is nested on the described interior input shaft (I1);
The first output shaft (TW1) and the second output shaft (TW2);
First clutch (C1) and second clutch (C2), described first clutch (C1) is located at an end of described interior input shaft (I1), and described second clutch (C2) is located at described outer input shaft (I2) end; It is characterized in that:
Be fixed with successively one grade of driving gear (1), third speed drive gear (2) and five grades of driving gears (3) on the other end of described interior input shaft (I1), described five grades of driving gears (3) are simultaneously as seven grades of driving gears;
Be fixed with successively fourth gear driving gear (4) and second gear driving gear (5) on the other end of described outer input shaft (I2), described fourth gear driving gear (4) is simultaneously as six grades of driving gears, and described second gear driving gear (5) is simultaneously as reverse driving gear;
Be provided with successively first speed driven gear (6), five grades of driven gears (7), fourth gear driven gear (8), reverse gear driven gear (9) and the first output gear (15) on described the first output shaft (TW1), wherein said first speed driven gear (6), five grades of driven gears (7), fourth gear driven gear (8), reverse gear driven gear (9) empty set and can be rotated around described the first output shaft (TW1) on described the first output shaft (TW1); Described the first output gear (15) is fixedly connected with described the first output shaft (TW1), is used for exporting the moment of torsion of the first output shaft (TW1); Be fixed with the first synchronizer (S1) on described the first output shaft (TW1) between described first speed driven gear (6) and the five grades of driven gears (7), optionally first grade of moment of torsion and the 5th grade of moment of torsion passed to the first output shaft (TW1); Be fixed with the second synchronizer (S2) on described the first output shaft (TW1) between described fourth gear driven gear (8) and the reverse gear driven gear (9), optionally fourth speed moment of torsion and reverse gear moment of torsion passed to the first output shaft (TW1);
Be provided with successively third gear driven gear (10), seven grades of driven gears (11), six grades of driven gears (12), second gear driven gear (13) and the second output gear (14) on described the second output shaft (TW2), wherein said third gear driven gear (10), seven grades of driven gears (11), six grades of driven gears (12) and second gear driven gear (13) empty set and can be rotated around the second output shaft (TW2) on described the second output shaft (TW2); Described the second output gear (14) is fixedly connected with described the second output shaft (TW2), is used for exporting the moment of torsion of described the second output shaft (TW2); Be fixed with the 3rd synchronizer (S3) on described the second output shaft (TW2) between described third gear driven gear (10) and the seven grades of driven gears (11), optionally third gear moment of torsion and the 7th grade of moment of torsion passed to described the second output shaft (TW2); Be fixed with the 4th synchronizer (S4) on described the second output shaft (TW2) between described six grades of driven gears (12) and the second gear driven gear (13), optionally the 6th grade of moment of torsion and second gear moment of torsion passed to described the second output shaft (TW2);
Described one grade of driving gear (1) is normal engagement with described first speed driven gear (6), described third speed drive gear (2) is normal engagement with described third gear driven gear (10), described five grades of driving gears (3) while and described five grades of driven gears (7), seven grades of driven gears (11) are normal engagement, described fourth gear driving gear (4) while and described fourth gear driven gear (8), six grades of driven gears (12) are normal engagement, described second gear driving gear (5) and described second gear driven gear (13) are normal engagement, and described second gear driven gear (13) and described reverse gear driven gear (9) are normal engagement.
2. transmission device of double clutch transmission according to claim 1 is characterized in that, also is provided with parking ratchet wheel (17) on described the first output shaft (TW1) or described the second output shaft (TW2) or the described differential mechanism (D).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220552439 CN202914643U (en) | 2012-10-26 | 2012-10-26 | Transmission device of double-clutch speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220552439 CN202914643U (en) | 2012-10-26 | 2012-10-26 | Transmission device of double-clutch speed changer |
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| Publication Number | Publication Date |
|---|---|
| CN202914643U true CN202914643U (en) | 2013-05-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220552439 Expired - Fee Related CN202914643U (en) | 2012-10-26 | 2012-10-26 | Transmission device of double-clutch speed changer |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103438159A (en) * | 2013-08-09 | 2013-12-11 | 浙江吉利汽车研究院有限公司 | Double-clutch automatic gearbox |
| WO2014067309A1 (en) * | 2012-10-31 | 2014-05-08 | 奇瑞汽车股份有限公司 | Dual clutch transmission |
| CN112413061A (en) * | 2019-08-20 | 2021-02-26 | 广州汽车集团股份有限公司 | Six-speed automatic transmission and vehicle |
-
2012
- 2012-10-26 CN CN 201220552439 patent/CN202914643U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014067309A1 (en) * | 2012-10-31 | 2014-05-08 | 奇瑞汽车股份有限公司 | Dual clutch transmission |
| US9618086B2 (en) | 2012-10-31 | 2017-04-11 | Chery Automobile Co., Ltd. | Dual-clutch transmission |
| CN103438159A (en) * | 2013-08-09 | 2013-12-11 | 浙江吉利汽车研究院有限公司 | Double-clutch automatic gearbox |
| CN112413061A (en) * | 2019-08-20 | 2021-02-26 | 广州汽车集团股份有限公司 | Six-speed automatic transmission and vehicle |
| CN112413061B (en) * | 2019-08-20 | 2024-04-19 | 广州汽车集团股份有限公司 | Six-speed automatic transmission and vehicle |
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| GR01 | Patent grant | ||
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Address after: Hefei City, Anhui Province, 230022 East Road No. 176 Patentee after: Anhui Jianghuai Automobile Group Limited by Share Ltd Address before: Hefei City, Anhui Province, 230022 East Road No. 176 Patentee before: Anhui Jianghuai Automobile Co., Ltd. |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130501 Termination date: 20201026 |