CN203822967U - Vertical double-clutch transmission actuator - Google Patents

Vertical double-clutch transmission actuator Download PDF

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Publication number
CN203822967U
CN203822967U CN201420259267.8U CN201420259267U CN203822967U CN 203822967 U CN203822967 U CN 203822967U CN 201420259267 U CN201420259267 U CN 201420259267U CN 203822967 U CN203822967 U CN 203822967U
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CN
China
Prior art keywords
gear
driving
driven
grades
input shaft
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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.)
Expired - Fee Related
Application number
CN201420259267.8U
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Chinese (zh)
Inventor
付永超
王维
丁兆福
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Anhui Jianghuai Automobile Group Corp
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Priority to CN201420259267.8U priority Critical patent/CN203822967U/en
Application granted granted Critical
Publication of CN203822967U publication Critical patent/CN203822967U/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Abstract

The utility model relates to a vertical double-clutch transmission actuator. Seen from an inner input shaft and an outer input shaft, gears are arranged in sequence as follows: a fourth-gear drive gear, a sixth-gear drive gear, a second-gear drive gear or a reverse-gear drive gear, a first-gear drive gear, a third-gear drive gear and a seventh-gear drive gear; the reverse-gear drive gear and the second-gear drive gear are the same gear, the low-speed large-torque gears (the first-gear drive gear and the reverse-gear drive gear) are arranged close to a gearbox casing in the middle of the actuator. Therefore, deformation of the input shafts during the operation is reduced, and the rigidity of the input shafts can be efficiently increased.

Description

A kind of vertical transmission device of double clutch transmission of putting
Technical field
The utility model belongs to automotive transmission technical field, is specifically related to the vertical transmission device of double clutch transmission of putting.
Background technique
To three-axle speed variator, the distance between input shaft and jack shaft 3 is speed changer centre distance, and its size is the boundary dimension to speed changer not only, volume and quality size, and the contact strength of the gear teeth is had to impact.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 arranged on housing through bearing, from arranging may considering with the intensity that does not affect housing with convenient of bearing, requires centre distance to get greatly.In addition be subject to the restriction that the third gear 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 after primary election centre distance, according to speed changer gear number, velocity ratio and transmission scheme, distribute each grade of gear number of teeth, then centre distance is revised, redistribute each grade of gear number of teeth.
Typical transmission device of double clutch transmission refers to by respectively with two input shafts of two clutches and is connected, and transmits engine power.Double clutch transmissions is by two groups of coaxial nested or clutches of being arranged in parallel, coaxially, two of inside and outside nested arrangement input shafts and an output shaft, a jack shaft being arranged in parallel with input shaft, is arranged in a plurality of synchronizers on input shaft and jack shaft, a plurality of reverse shift fork composition.Speed changer is strange, even number shelves input gear is arranged on two input shafts, and switching and different synchronizer by two clutches move, and via jack shaft, realize torque conversion and output.Existing indulging put double-clutch automatic gearbox transmission device, and the matching of speed changer centre distance and each grade of arrangement of gears is not fine, affects gear life.
Model utility content
The problem of mating with each grade of arrangement of gears in order to solve the centre distance of existing dual-clutch transmission existence, the utility model provides a kind of new structure transmission device of double clutch transmission.
The technical solution that the utility model is realized above-mentioned purpose is as follows:
Indulge and put a transmission device of double clutch transmission, comprising:
Coaxial interior input shaft, outer input shaft and the output shaft arranging, described outer input shaft is hollow shaft, is nested on described interior input shaft, on described output shaft, rigid connecting is connected to output shaft gear;
The jack shaft and the reverse gear shaft that are arranged in parallel with described interior input shaft and outer input shaft;
First clutch and second clutch, described first clutch connects described interior input shaft, and described second clutch connects described outer input shaft; It is characterized in that:
On described interior input shaft, be provided with successively one grade of driving gear, third speed drive gear and seven grades of driving gears, on described outer input shaft, be provided with successively fourth gear driving gear, six grades of driving gears and second gear driving gear, described second gear driving gear is simultaneously as reversing gear driving gear, wherein, described fourth gear driving gear and described six grades of driving gears by bearings on described outer input shaft, described seven grades of driving gears by bearings on described interior input shaft, described second gear driving gear is rigidly attached on described outer input shaft, described one grade of driving gear, described third speed drive gear is rigidly attached on described interior input shaft 1, between described fourth gear driving gear and described six grades of driving gears, arranged the first synchronizer SC1, described seven grades of driving wheel rear ends are provided with the 4th synchronizer SC4,
On described jack shaft, be provided with successively fourth gear driven gear, six grades of driven gears, second gear driven gear, reverse gear driven gear, first speed driven gear, third gear driven gear, seven grades of driven gears and countershaft-gear, wherein, described fourth gear driven gear, six grades of driven gears, seven grades of driven gears and countershaft-gear are rigidly attached on described jack shaft, described second gear driven gear, reverse gear driven gear, first speed driven gear and third gear driven gear all by bearings on described jack shaft, between described second gear driven gear and described reverse gear driven gear, arranged the second synchronizer SC2, between described first speed driven gear and described third gear driven gear, arranged the 3rd synchronizer SC3, the second synchronizer SC2 and SC3 and jack shaft are rigidly connected,
On described reverse gear shaft, rigid connecting is connected to reverse gear one, reverse gear two;
Described countershaft-gear and described output shaft gear are normal engagement, described seven grades of driving gears and described seven grades of driven gears are normal engagement, described third speed drive gear and described third gear driven gear often mesh, described one grade of driving gear and described first speed driven gear are normal engagement, described second gear driving gear and described second gear driven gear, described reverse gear one is normal engagement, described reverse gear two is normal engagement with described reverse gear driven gear, described six grades of driving gears and described six grades of driven gears are normal engagement, described fourth gear driving gear and described fourth gear driven gear are normal engagement.
Useful technique effect of the present utility model embodies in the following areas:
Each grade of gear carried out meticulous layout, and the matching of each grade of arrangement of gears and centre distance is better.
Accompanying drawing explanation
Fig. 1 is the vertical transmission device of double clutch transmission structural representation of putting of the present embodiment.
Mark in upper figure: 1, interior input shaft, 2, outer input shaft, 3, jack shaft, 4, output shaft, 5, reverse gear shaft, 11, one grade of driving gear, 22, second gear driving gear, 13, third speed drive gear, 24, fourth gear driving gear, 26, six grades of driving gears, 17, seven grades of driving gears, 31, first speed driven gear, 32, second gear driven gear, 33, third gear driven gear, 34, fourth gear driven gear, 36, six grades of driven gears, 37, seven grades of driven gears, 39, reverse gear driven gear, 30, countershaft-gear, 40, output shaft gear, 51, reverse gear one, 52, reverse gear two, the first synchronizer SC1, the second synchronizer SC2, the 3rd synchronizer SC3, the 4th synchronizer SC4, first clutch C1, second clutch C2.
Embodiment
Below in conjunction with accompanying drawing, by embodiment, the utility model is further described.
Referring to Fig. 1, first clutch C1 is connected with interior input shaft 1, second clutch C2 is connected with outer input shaft 2, by the open and close controlling of first clutch C1 and C2, can selectively motor (not showing in Fig. 1) moment of torsion be delivered to interior input shaft 1 and outer input shaft 2.On interior input shaft 1 from left to right (near motor one side for left, away from motor one side for right) arranging successively one grade of driving gear 11, third speed drive gear 13, seven grades of driving gears 17; On outer input shaft 2, arranging successively from left to right fourth gear driving gear 24, six grades of driving gears 26 and second gear driving gears 22, wherein, second gear driving gear 22 is used as reverse driving gear simultaneously and uses.Like this, from whole input shaft assembly 1,2, odd number shelves driving gear is disposed on interior input shaft 1, and even number shelves and reverse driving gear are disposed on outer input shaft 2.From left to right (Fig. 1 shows, near motor one side be left, away from motor one side, be the right side), arrangement of gears is sequentially followed successively by: fourth gear driving gear 24, six grades of driving gears 26, second gear driving gear 22, one grade of driving gear 11, third speed drive gear 13, seven grades of driving gears 17.Wherein, fourth gear driving gear 24 and six grades of driving gears 26 are by bearings outside on input shaft 2, seven grades of driving gears 17 by bearings on interior input shaft 1, second gear driving gear 22 is rigidly connected outside on input shaft 2, and one grade of driving gear 11, third speed drive gear 13 are rigidly attached on interior input shaft 1.Between fourth gear driving gear 24 and six grades of driving gears 26, arranged the first synchronizer SC1, this device is rigidly connected outside on input shaft 2, can be optionally by 2 transmission of power on outer input shaft on fourth gear driving gear 24 or six grades of driving gears 26; Seven grades of driving wheel 17 rear ends, the 4th synchronizer SC4 is installed, this device is rigidly attached on input shaft 1, can be optionally by transmission of power to the seven grade driving gear 17 on interior input shaft 1 or output shaft 4.
Output shaft 4 and input shaft 1 coaxial line layout, on it, rigid connecting is connected to output shaft gear 40.
Jack shaft 3 and input shaft 1,2 are arranged in parallel, from left to right (near motor one side for left, away from motor one side for right) be provided with fourth gear driven gear 34, six grades of driven gears 36, second gear driven gear 32, reverse gear driven gear 39, first speed driven gear 31, third gear driven gear 33, seven grades of driven gears 37 and countershaft-gears 30.Wherein, fourth gear driven gear 34, six grades of driven gears 36, seven grades of driven gears 37 and countershaft-gear 30 are rigidly attached on jack shaft 3.Second gear driven gear 32, reverse gear driven gear 39, first speed driven gear 31 and third gear driven gear 33 all by bearings on jack shaft 3.Between second gear driven gear 32 and reverse gear driven gear 39, arranged the second synchronizer SC2, between first speed driven gear 31 and third gear driven gear 33, arranged the 3rd synchronizer SC3, the second synchronizer SC2 and SC3 and jack shaft 3 are rigidly connected, and these two synchromesh gears can optionally optionally be delivered to the power of second gear driven gear 32, reverse gear driven gear 39, first speed driven gear 31 and third gear driven gear 33 on jack shaft 3.
Reverse gear shaft 5 is arranged in parallel with input shaft 1,2, and on it, (near motor one side, for a left side, away from motor one side, being right) is provided with reverse gear 1, reverse gear 2 52 from left to right, and these two gears are rigidly attached on reverse gear shaft 5.
Countershaft-gear 30 is normal engagement with output shaft gear 40, seven grades of driving gears 17 and seven grades of driven gears 37 are normal engagement, third speed drive gear 13 often meshes with third gear driven gear 33, one grade of driving gear 11 is normal engagement with first speed driven gear 31, second gear driving gear 22 is normal engagement with second gear driven gear 32, reverse gear 1, reverse gear 2 52 is normal engagement with reverse gear driven gear 39, six grades of driving gears 26 and six grades of driven gears 36 are normal engagement, and fourth gear driving gear 24 is normal engagement with fourth gear driven gear 34.
Power transmission line explanation:
One grade of power transmission line: the 3rd synchronizer SC3 and first speed driven gear 31 combinations, first clutch C1 is closed, Engine torque passes to interior input shaft 1 by first clutch C1, via one grade of driving and driven gear 11,31 of normal engagement and the 3rd synchronizer SC3, transfer torque to jack shaft 3, by countershaft-gear 30 and output shaft gear 40, moment of torsion is passed to output shaft 4 again, and finally by output shaft 4 outputting powers.
Second gear power transmission line: the second synchronizer SC2 and 22 combinations of second gear driving gear, second clutch C2 is closed, Engine torque passes to outer input shaft 2 by second clutch C2, via the second synchronizer SC2 and the driving and driven gear 22,32 of the normal engagement of second gear, transfer torque to jack shaft 3, by countershaft-gear 30 and output shaft gear 40, moment of torsion is passed to output shaft 4 again, and finally by output shaft 4 outputting powers.
Third gear power transmission line: the 3rd synchronizer SC3 and 33 combinations of third gear driven gear, first clutch C1 is closed, Engine torque passes to interior input shaft 1 by first clutch C1, via the third gear driving and driven gear 13,33 of normal engagement and the 3rd synchronizer SC3, transfer torque to jack shaft 3, by countershaft-gear 30 and output shaft gear 40, moment of torsion is passed to output shaft 4 again, and finally by output shaft 4 outputting powers.
Fourth gear power transmission line: the first synchronizer SC1 and 34 combinations of fourth gear driven gear, second clutch C2 is closed, Engine torque passes to outer input shaft 2 by second clutch C2, via the fourth gear driving and driven gear 24,34 of normal engagement and the first synchronizer SC1, transfer torque to jack shaft 3, by countershaft-gear 30 and output shaft gear 40, moment of torsion is passed to output shaft 4 again, and finally by output shaft 4 outputting powers.
Five grades of power transmission lines: the 4th synchronizer SC4 and output shaft 4 combinations, Engine torque passes to interior input shaft 1 by first clutch C1, via the 4th synchronizer SC4, moment of torsion is passed to output shaft 4, and finally by output shaft 4 outputting powers.
Six grades of power transmission lines: the first synchronizer SC1 and six grades of driving gear 26 combinations, second clutch C2 is closed, Engine torque passes to outer input shaft 2 by second clutch C2, via the first synchronizer SC1 and six grades of driving and driven gears 26,36 of normal engagement, transfer torque to jack shaft 3, by countershaft-gear 30 and output shaft gear 40, moment of torsion is passed to output shaft 4 again, and finally by output shaft 4 outputting powers.
Seven grades of power transmission lines: the 4th synchronizer SC4 and seven grades of driving gear 17 combinations, first clutch C1 is closed, Engine torque passes to interior input shaft 1 by first clutch C1, via the 4th synchronizer SC4 and seven grades of driving and driven gears 17,37 of normal engagement, transfer torque to jack shaft 3, by countershaft-gear 30 and output shaft gear 40, moment of torsion is passed to output shaft 4 again, and finally by output shaft 4 outputting powers.
Reverse gear transfer route: the second synchronizer SC2 and 39 combinations of reverse gear driven gear, second clutch C2 is closed, Engine torque passes to outer input shaft 2 by second clutch C2, through reverse gear, often mesh driving gear 22, reverse gear 1, be delivered on reverse gear shaft 5, through constant mesh gear 52,39 and the second synchronizer SC2, transmission of power is arrived to jack shaft 3, then by countershaft-gear 30 and output shaft gear 40, moment of torsion is being passed to output shaft 4, and finally by output shaft 4 outputting powers.
Gearshift procedure illustrates:
One grade is changed second gear process: dual-clutch transmission is in one grade, the 3rd synchronizer SC3 and first speed driven gear 31 combinations, and first clutch C1 is closed, and second clutch C2 opens; Dual-clutch transmission control system (not showing in accompanying drawing 1) is sent one grade and is changed second gear instruction, gear-shifting actuating mechanism is in advance by the second synchronizer SC2 and 32 combinations of second gear driven gear, now second clutch C2 is still in open mode, i.e. second clutch C2 and outer input shaft 2 transferring power not; Along with gearshift procedure continues, first clutch C1 opens gradually, and meanwhile, second clutch C2 is closed gradually, and this process there will not be torque break; First clutch C1 opens completely, after the complete closure of second clutch C2, the 3rd synchronizer SC3 throws off the combination with first speed driven gear 31, finish gearshift procedure, Engine torque is via second clutch C2, outer input shaft 2, second gear driving gear 22, second gear driven gear 32, the second synchronizer SC2, jack shaft 3, countershaft-gear 30, output shaft gear 40, finally exported by output shaft 4.
In the utility model double clutch transmissions, from whole input shaft 1, 2, (near starting pusher side, be left from left to right, away from starting pusher side, being right) arrangement of gears is sequentially followed successively by: fourth gear driving gear 24, six grades of driving gears 26, second gear and reverse driving gear 22, one grade of driving gear 11, third speed drive gear 13, seven grades of driving gears 17, reverse driving gear and second gear driving gear are same gears 22, low-speed big gear (one, reverse gear) arrange the gear box casing near neutral position, be conducive to reduce the distortion of input shaft when work, effectively increased the rigidity of input shaft.
Although the utility model is described in conjunction with above embodiment, but the utility model is not limited to above-described embodiment, and be only subject to the restriction of claim, those of ordinary skills can easily modify to it and change, but do not leave essence design of the present utility model and scope.

Claims (1)

1. indulge and put a transmission device of double clutch transmission, comprising:
Coaxial interior input shaft, outer input shaft and the output shaft arranging, described outer input shaft is hollow shaft, is nested on described interior input shaft, on described output shaft, rigid connecting is connected to output shaft gear;
The jack shaft and the reverse gear shaft that are arranged in parallel with described interior input shaft and outer input shaft;
First clutch and second clutch, described first clutch connects described interior input shaft, and described second clutch connects described outer input shaft; It is characterized in that:
On described interior input shaft, be provided with successively one grade of driving gear, third speed drive gear and seven grades of driving gears, on described outer input shaft, be provided with successively fourth gear driving gear, six grades of driving gears and second gear driving gear, described second gear driving gear is simultaneously as reversing gear driving gear, wherein, described fourth gear driving gear and described six grades of driving gears by bearings on described outer input shaft, described seven grades of driving gears by bearings on described interior input shaft, described second gear driving gear is rigidly attached on described outer input shaft, described one grade of driving gear, described third speed drive gear is rigidly attached on described interior input shaft 1, between described fourth gear driving gear and described six grades of driving gears, arranged the first synchronizer SC1, described seven grades of driving wheel rear ends are provided with the 4th synchronizer SC4,
On described jack shaft, be provided with successively fourth gear driven gear, six grades of driven gears, second gear driven gear, reverse gear driven gear, first speed driven gear, third gear driven gear, seven grades of driven gears and countershaft-gear, wherein, described fourth gear driven gear, six grades of driven gears, seven grades of driven gears and countershaft-gear are rigidly attached on described jack shaft, described second gear driven gear, reverse gear driven gear, first speed driven gear and third gear driven gear all by bearings on described jack shaft, between described second gear driven gear and described reverse gear driven gear, arranged the second synchronizer SC2, between described first speed driven gear and described third gear driven gear, arranged the 3rd synchronizer SC3, the second synchronizer SC2 and SC3 and jack shaft are rigidly connected,
On described reverse gear shaft, rigid connecting is connected to reverse gear one, reverse gear two;
Described countershaft-gear and described output shaft gear are normal engagement, described seven grades of driving gears and described seven grades of driven gears are normal engagement, described third speed drive gear and described third gear driven gear often mesh, described one grade of driving gear and described first speed driven gear are normal engagement, described second gear driving gear and described second gear driven gear, described reverse gear one is normal engagement, described reverse gear two is normal engagement with described reverse gear driven gear, described six grades of driving gears and described six grades of driven gears are normal engagement, described fourth gear driving gear and described fourth gear driven gear are normal engagement.
CN201420259267.8U 2014-05-19 2014-05-19 Vertical double-clutch transmission actuator Expired - Fee Related CN203822967U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201420259267.8U CN203822967U (en) 2014-05-19 2014-05-19 Vertical double-clutch transmission actuator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201420259267.8U CN203822967U (en) 2014-05-19 2014-05-19 Vertical double-clutch transmission actuator

Publications (1)

Publication Number Publication Date
CN203822967U true CN203822967U (en) 2014-09-10

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CN201420259267.8U Expired - Fee Related CN203822967U (en) 2014-05-19 2014-05-19 Vertical double-clutch transmission actuator

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110864088A (en) * 2018-08-28 2020-03-06 长城汽车股份有限公司 Speed change mechanism, dual-clutch transmission and vehicle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110864088A (en) * 2018-08-28 2020-03-06 长城汽车股份有限公司 Speed change mechanism, dual-clutch transmission and vehicle

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Legal Events

Date Code Title Description
C14 Grant of patent or utility model
GR01 Patent grant
C56 Change in the name or address of the patentee
CP01 Change in the name or title of a patent holder

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

Patentee after: Anhui Jianghuai Automobile Group Limited by Share Ltd

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

Patentee before: Anhui Jianghuai Automobile Co., Ltd.

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: 20140910

Termination date: 20190519