CN103836126B - A kind of automobile double clutch variator - Google Patents

A kind of automobile double clutch variator Download PDF

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Publication number
CN103836126B
CN103836126B CN201410127289.3A CN201410127289A CN103836126B CN 103836126 B CN103836126 B CN 103836126B CN 201410127289 A CN201410127289 A CN 201410127289A CN 103836126 B CN103836126 B CN 103836126B
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China
Prior art keywords
gear
follower
grades
output shaft
gears
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Active
Application number
CN201410127289.3A
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Chinese (zh)
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CN103836126A (en
Inventor
罗素·莱蒙
戴维·山侬-胡普尔
李宇栋
曾华庆
李玉锋
林健
桑芾生
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Chery Holdings Limited
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Chery Automobile Co Ltd
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Priority to CN201410127289.3A priority Critical patent/CN103836126B/en
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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
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • 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
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • 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
    • F16H2200/00Transmissions for multiple ratios
    • F16H2200/003Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds

Abstract

The present invention discloses a kind of automobile double clutch variator, first output shaft (5) and the 2nd output shaft (28) are provided with one, and the intermeshing back gear for reverse gear is secondary, and two gears of described back gear pair are the floating gear of empty set on corresponding axle; Back gear 10 on first output shaft (5) is also provided with one for realizing the reverse gear synchronizer (9) of multiple reverse gear speed ratio. Adopt technique scheme, compared with prior art, adopt two output shafts, it is possible to realize seven advance shelves, at least one reverse gear and a neutral gear, and reverse gear speed ratio is bigger; It is axially apart from short, and reasonable structural arrangement, meets simple, compact requirement.

Description

A kind of automobile double clutch variator
Technical field
The invention belongs to the technical field of automotive transmission. More specifically, the present invention relates to a kind of automobile double clutch variator.
Background technology
Dual-clutch transmission adopts double clutch construction and fixed axis gear transmission, with hydraulic automatic speed variator (AT, and stepless automatic transmission device (CVT AutomaticTransmission), ContinuouslyVariableTransmission) compare, its transmission efficiency height, oil consumption is low, solves electric control mechanical type automatic speed variator (AMT simultaneously, AutomatedManualTransmission) there is the shortcoming of power interruption, significantly improve and drive comfortable property. Therefore the focus of wheel box industry development is progressively become.
Chinese patent CN102308120A discloses a kind of seven speed dual clutch transmission, this dual-clutch transmission is provided with large diameter gear and small-diameter gear on second gear follower gear, large diameter gear engages with second gear driving toothed gear, and small-diameter gear engages with back gear, to realize reverse gear speed ratio. Obviously, the limited size of back gear is in the distance of the external diameter of the 2nd input shaft and the center of the first output shaft, the distance of the first output shaft and the 2nd output shaft also limit the speed ratio of intermeshing small-diameter gear and back gear on this diaxon simultaneously, and namely reverse gear speed ratio (input speed/output speed) is less.
Summary of the invention
The present invention provides a kind of automobile double clutch variator, its objective is to realize multiple reverse gear ratio by means of only two output shafts, and reverse gear speed ratio is relatively big, simultaneously its reasonable structural arrangement, simple, compact.
For achieving the above object, the present invention takes following technical scheme:
The automobile double clutch variator of the present invention, comprises the first clutch coupling, the 2nd clutch coupling, the first input shaft, the 2nd input shaft, the first output shaft, the 2nd output shaft;
2nd input shaft is tubular shaft, coaxially air-ground is enclosed within the first input shaft;
Engine power axle by the first clutch coupling with first input shaft engage or be separated; Engine power axle by the 2nd clutch coupling with the 2nd input shaft engage or be separated;
First output shaft is arranged in the both sides of the 2nd input shaft parallelly with the 2nd output shaft;
The first described input shaft and the 2nd input shaft are respectively equipped with multiple driving toothed gear being fastenedly connected with it, the first described output shaft and the 2nd output shaft are respectively equipped with the follower gear of multiple empty set on corresponding axle; Described follower gear engages with corresponding driving toothed gear;
The first described output shaft is provided with first and main subtracts driving toothed gear, and the first main driving toothed gear that subtracts subtracts follower gear with the master on differential mechanism and engages; The 2nd described output shaft is provided with the 2nd and main subtracts driving toothed gear, and the 2nd main driving toothed gear that subtracts also subtracts follower gear with described master and engages;
The first described output shaft and the 2nd output shaft are respectively equipped with for controlling joint and the advance shelves synchronizer being separated between described follower gear and the output shaft at its place;
Also being provided with one to the intermeshing back gear pair for reverse gear on the first described output shaft and the 2nd output shaft, two gears of described back gear pair are the floating gear of empty set on corresponding axle;
The reverse drive gear being positioned on the first described output shaft is also provided with one for realizing the reverse gear synchronizer of multiple reverse gear speed ratio.
Described driving toothed gear comprises three or the five grades of driving toothed gears being located on the first input shaft, one grade of driving toothed gear and seven grades of driving toothed gears, and the six grades of driving toothed gears, second gear driving toothed gear and the fourth gear driving toothed gear that are located on the 2nd input shaft;
Described follower gear comprises the second gear follower gear, third gear follower gear and the one grade of follower gear that are located on the first output shaft, and the six grades of follower gears being located on the 2nd output shaft, fourth gear follower gear, five grades of follower gears and seven grades of follower gears;
Described second gear follower gear engages with second gear driving toothed gear; Third gear follower gear engages with three or five grades of driving toothed gears; One grade of follower gear engages with one grade of driving toothed gear;
Six grades of described follower gears engage with six grades of driving toothed gears; Fourth gear follower gear engages with fourth gear driving toothed gear; Five grades of follower gears engage with three or five grades of driving toothed gears; Seven grades of follower gears engage with seven grades of driving toothed gears.
Two gears of described back gear pair are respectively: the back gear being located on the first output shaft and the reverse gear follower gear being located on the 2nd output shaft.
Described reverse gear follower gear and five grades of follower gears are coaxially fixed together.
Described advance shelves synchronizer comprise be located on the first output shaft for controlling the second gear synchronizer that second gear follower gear and the first output shaft are separated and engage; Described second gear synchronizer is arranged on described second gear follower gear and master subtracts between driving toothed gear or between described second gear follower gear and back gear.
Described reverse gear synchronizer is arranged between described second gear follower gear and back gear, for the joint that controls described second gear follower gear and back gear be separated.
Described advance shelves synchronizer comprise be located on the first output shaft, for controlling the third gear synchronizer that one grade of follower gear and third gear follower gear and the first output shaft are separated and engage, a described third gear synchronizer is arranged between described one grade follower gear and third gear follower gear
Described advance shelves synchronizer comprise be located on the 2nd output shaft, for controlling four or six grades of synchronizers that fourth gear follower gear is separated with six grades of follower gears and the 2nd output shaft and engages, four or six grades of described synchronizers are arranged between described fourth gear follower gear and six grades of follower gears.
Described advance shelves synchronizer comprise be located on the 2nd output shaft, for controlling five or seven grades of synchronizers that five grades of follower gears are separated with seven grades of follower gears and the 2nd output shaft and engage, five or seven grades of described synchronizers are arranged between described five grade follower gear and seven grades of follower gears.
The radial dimension of described one grade of follower gear, second gear follower gear, third gear follower gear, fourth gear follower gear, five grades of follower gears, six grades of follower gears and back gear makes the sliding cover of corresponding synchronizer can partly embed in corresponding teeth portion.
The first described output shaft or the 2nd output shaft are provided with the parking wheel being fixedly connected with it.
The present invention adopts technique scheme, compared with prior art, adopts two output shafts, it is possible to realize seven advance shelves, at least one reverse gear and a neutral gear, and reverse gear speed ratio is bigger; It is axially apart from short, and reasonable structural arrangement, meets simple, compact requirement.
Accompanying drawing explanation
Fig. 1 is the expansion schematic diagram of transmission rig of the present invention;
Fig. 2 is the side schematic view of structure shown in Fig. 1.
Figure is labeled as:
1, first input shaft, 2, 2nd input shaft, 3, six grades of driving toothed gears, 4, second gear driving toothed gear, 5, first output shaft (A1), 6, first output shaft master subtracts driving toothed gear, 7, second gear synchronizer (S2), 8, second gear follower gear, 9, reverse gear synchronizer (SR), 10, back gear, 11, third gear follower gear, 12, one grade of follower gear, 13, one third gear synchronizer (S13), 14, parking is taken turns, and 15, fourth gear driving toothed gear, 16, three or five grades of driving toothed gears, 17, one grade of driving toothed gear, 18, five reverse gear follower gears, 18a, reverse gear follower gear, 18b, five grades of follower gears, 19, seven grades of driving toothed gears, 20, seven grades of follower gears, 21, five or seven grades of synchronizers (S57), 22, fourth gear follower gear, 23, four or six grades of synchronizers (S46), 24, six grades of follower gears, 25, differential mechanism, 26, master subtracts follower gear, 27, 2nd output shaft master subtracts driving toothed gear, 28, 2nd output shaft (A2), 29, engine power axle, C1, first clutch coupling, C2, 2nd clutch coupling, D1, one grade, D2, second gear, D3, third gear, D4, fourth gear, D5, five grades, D6, six grades, D7, seven grades, R, reverse gear.
Embodiment
Compare accompanying drawing below, by the description to embodiment, the specific embodiment of the present invention is described in further detail, to help the technician of this area that invention design, the technical scheme of the present invention are had more complete, accurate and deep understanding.
As shown in Figure 1 and Figure 2, it is a kind of automobile double clutch speed changer structure of the present invention. Specifically, it is for the horizontal seven speed dual clutch transmission putting forerunner's automobile of engine. This variator comprises two clutch couplinges, two transmission shafts, two drive shafts and a differential mechanism. Specifically comprise the first input shaft 1, the 2nd input shaft 2; First clutch coupling C1, the 2nd clutch coupling C2; First output shaft 5, the 2nd output shaft 28, differential mechanism 25;
2nd input shaft 2 is tubular shaft, coaxially air-ground is enclosed within the first input shaft 1;
Engine power axle 29 is engaged by the first clutch coupling C1 with the first input shaft 1 or is separated; Engine power axle 29 is engaged by the 2nd clutch coupling C2 with the 2nd input shaft 2 or is separated, it is achieved transmission of power;
First output shaft 5 is arranged in the both sides of the 2nd input shaft 2 parallelly with the 2nd output shaft 28;
Differential mechanism 25 input terminus is provided with master and subtracts follower gear 26; First output shaft 5 is provided with the first master and subtracts driving toothed gear 6, and the 2nd output shaft 28 is provided with the 2nd master and subtracts driving toothed gear 27. That is: the first main driving toothed gear 6 that subtracts subtracts follower gear 26 with leading and engages; 2nd main subtract driving toothed gear 27 and also subtracts follower gear 26 engage with leading.
In order to solve prior art Problems existing and overcome its defect, it is achieved reasonable structural arrangement, simple, compact goal of the invention, the technical scheme that the present invention takes is:
As shown in Figure 1 and Figure 2, the automobile double clutch variator of the present invention, the first described input shaft 1 and the 2nd input shaft 2 are respectively equipped with multiple driving toothed gear being fastenedly connected with it, the first described output shaft 5 and the 2nd output shaft 28 are respectively equipped with the follower gear of multiple empty set on corresponding axle; Described follower gear engages with corresponding driving toothed gear.
Described driving toothed gear comprises three or five grades of driving toothed gears, 16, one grade of driving toothed gear 17 and seven grades of driving toothed gears 19 of being located on the first input shaft 1, and the six grades of driving toothed gears 3, second gear driving toothed gear 4 and the fourth gear driving toothed gear 15 that are located on the 2nd input shaft 2.
Described follower gear comprises the second gear follower gear 8, third gear follower gear 11 and the one grade of follower gear 12 that are located on the first output shaft 5, and the six grades of follower gears 24 being located on the 2nd output shaft 28, fourth gear follower gear 22, five grades of follower gear 18b and seven grade of follower gears 20;
Described second gear follower gear 8 engages with second gear driving toothed gear 4; Third gear follower gear 11 engages with three or five grades of driving toothed gears 16; One grade of follower gear 12 engages with one grade of driving toothed gear 17;
Six grades of described follower gears 24 engage with six grades of driving toothed gears 3; Fourth gear follower gear 22 engages with fourth gear driving toothed gear 15; Five grades of follower gear 18b engage with three or five grades of driving toothed gears 16; Seven grades of follower gears 20 engage with seven grades of driving toothed gears 19.
Variator the 3rd and fifth speed adopt and share driving toothed gear, it is possible to shorten the axial distance of wheel box.
Also being provided with one to the intermeshing back gear pair for reverse gear on the first described output shaft 5 and the 2nd output shaft 28, two gears of described back gear pair are the floating gear of empty set on corresponding axle; Back gear pair is respectively: the back gear 10 being located on the first output shaft 5 and the reverse gear follower gear 18a being located on the 2nd output shaft 28.
Described reverse gear follower gear 18a and five grade of follower gear 18b is coaxially fixed together.
The first described output shaft 5 is multiple with being respectively equipped with on the 2nd output shaft 28 to be engaged and the advance shelves synchronizer being separated with the output shaft at its place for controlling described follower gear.
Described advance shelves synchronizer comprise be located on the first output shaft 5, for controlling between second gear follower gear 8 with the first output shaft 5 the second gear synchronizer 7 being separated and engaging. In a preferred embodiment, second gear synchronizer 7 is arranged on described second gear follower gear 8 and master subtracts between driving toothed gear 6, and alternative embodiment is: described second gear synchronizer 7 is arranged between described second gear follower gear 8 and back gear 10.
Described advance shelves synchronizer comprise be located on the first output shaft 5, for controlling the third gear synchronizer 13 that one grade of follower gear 12 is separated with third gear follower gear 11 and the first output shaft 5 and engages; A described third gear synchronizer 13 is arranged between described one grade follower gear 12 and third gear follower gear 11.
Described advance shelves synchronizer comprise be located on the 2nd output shaft 28, for controlling four or six grades of synchronizers 23 that fourth gear follower gear 22 is separated with six grades of follower gears 24 and the 2nd output shaft 28 and engages; Four or six grades of described synchronizers 23 are arranged between described fourth gear follower gear 22 and six grades of follower gears 24.
Described advance shelves synchronizer comprise be located on the 2nd output shaft 28, for controlling five or seven grades of synchronizers 21 that five grades of follower gear 18b are separated with seven grades of follower gears 20 and the 2nd output shaft 28 and engage; Five or seven grades of described synchronizers 21 are arranged between described five grade follower gear 18b and seven grade of follower gear 20.
It is positioned on the reverse drive gear 10 of the first output shaft 5 and also it is provided with one for realizing the reverse gear synchronizer 9 of multiple reverse gear speed ratio, engaging with back gear 10 for controlling described second gear follower gear 8 and be separated, described reverse gear synchronizer 9 is arranged between described second gear follower gear 8 and back gear 10.
The first described output shaft 5 or the 2nd output shaft 28 are provided with the parking wheel 14 being fixedly connected with it, that is: parking wheel 14 is fixed therein on an output shaft, reliable parking during to ensure to hang P shelves.
For the radial dimension of the empty set gear of the major part floating on minimizing axial length, the first output shaft 5 and the 2nd output shaft 28 can be designed to enough big, during to meet synchronizer joint, the sliding cover of synchronizer can partly embed gear inside. These empty set gears comprise second gear follower gear 8, back gear 10, third gear follower gear 11, one grade of follower gear, 12, five grades of follower gear 18b, fourth gear follower gear 22 and six grades of follower gears 24.
When being linked into D shelves, engaging the synchronizer of forward, make the follower gear of corresponding forward interconnected with the output shaft at its place, then switch clutch obtains input moment of torsion, namely by the combination of the clutch coupling advised and synchronizer, it is possible to realize seven advance shelves.
One grade realizes in the following manner:
As shown in Figure 1, move to right the sliding cover of a third gear synchronizer 13, engage the first clutch coupling C1, moment of torsion is passed to successively the first input shaft 1, one grade of driving toothed gear 17, one grade of follower gear 12, first output shaft 5, first output shaft master and subtracts driving toothed gear 6 and main subtract follower gear 26. The optimization of speed ratio can be realized by adjusting the size of each gear.
Similarly, by engaging, corresponding synchronizer and clutch coupling realize other forward.
When being linked into R shelves, except engaged reverse synchronizer 9, the synchronizer of a certain odd gear need to be engaged simultaneously, namely at least can realize a reverse gear, it is preferable that engage one grade of synchronizer, to obtain maximum reverse gear speed ratio.
Reverse gear realizes in the following manner:
Engage clutch coupling C2, moment of torsion is passed to successively the 2nd input shaft 2, second gear driving toothed gear 4, second gear follower gear 8; Engaged reverse synchronizer 9, back gear 10 transmits moment of torsion with the synchronized rotation of second gear follower gear 8. Moment of torsion is delivered to back gear 10, then to reverse gear follower gear 18a, then to five grades of follower gear 18b. Now, the rotary speed direction of five grades of follower gear 18b with its when advance shelves contrary, so far, concrete correspondence can realize four reverse gear speed ratios in conjunction with different odd number shelves.
It is as follows that preferred reverse gear implements mode:
Moment of torsion is passed to three or five grades of driving toothed gears 16, first input shaft, 1, one grade of driving toothed gear 17 and one grade of follower gear 12 successively by five grades of follower gear 18b; Move to right the sliding cover of a third gear synchronizer 13, one grade of follower gear 12 and the first synchronized rotation of output shaft 5, transmit moment of torsion to the first output shaft master and subtract driving toothed gear 6, finally reach master and subtract follower gear 26.
This preferred version can obtain maximum reverse gear speed ratio, and without the need to operating synchronizer, only by the 2nd clutch coupling C2, input moment of torsion is switched to the first clutch coupling C1 and can realize one grade. The reverse gear speed ratio scope of the dual-clutch transmission in existing market is 14-18, and the reverse gear speed ratio of the program can reach more than 20.
Alternative reverse gear speed ratio realizes by the synchronizer of other odd gear engaged except a grade, namely uses third gear, five grades or seven grades of gear pairs transmission moments of torsion.
In sum, the concrete moment of torsion transfer route of each shelves position of the present invention is respectively:
One grade of operation: engine power axle 29, first clutch coupling C1, the first input shaft 1, grade driving toothed gear 17, grade follower gear 12, third gear synchronizer 13, first output shaft 5, first is main subtracts driving toothed gear 6, and master subtracts follower gear 26, differential mechanism 25.
Second gear runs: engine power axle the 29, two clutch coupling C2, the 2nd input shaft 2, second gear driving toothed gear 4, second gear follower gear 8, and second gear synchronizer 7, first output shaft 5, first is main subtracts driving toothed gear 6, and master subtracts follower gear 26, differential mechanism 25.
Third gear is run: engine power axle 29, first clutch coupling C1, the first input shaft 1,35 grades of driving toothed gears 16, and third gear follower gear 11, third gear synchronizer 13, first output shaft 5, first is main subtracts driving toothed gear 6, and master subtracts follower gear 26, differential mechanism 25.
Fourth gear is run: engine power axle the 29, two clutch coupling C2, the 2nd input shaft 2, fourth gear driving toothed gear 15, and fourth gear follower gear 22,46 grades of synchronizer the 23, two output shafts the 28, two are main subtracts driving toothed gear 27, and master subtracts follower gear 26, differential mechanism 25.
Five grades of operations: engine power axle 29, first clutch coupling C1, the first input shaft 1,35 grades of driving toothed gears, 16, five grades of follower gear 18b, five or seven grades of synchronizer the 21, two output shaft the 28, two masters subtract driving toothed gear 27, and master subtracts follower gear 26, differential mechanism 25.
Six grades of operations: engine power axle the 29, two clutch coupling C2, the 2nd input shaft 2, six grades of driving toothed gears, 3, six grades of follower gears 24,46 grades of synchronizer the 23, two output shafts the 28, two masters subtract driving toothed gear 27, and master subtracts follower gear 26, differential mechanism 25.
Seven grades of operations: engine power axle 29, first clutch coupling C1, first input shaft 1, seven grades driving toothed gear 19, seven grades of follower gears 20,57 grades synchronizer the 21, two output shaft the 28, two is main subtracts driving toothed gear 27, and master subtracts follower gear 26, differential mechanism 25.
Preferred reverse gear runs drive path: engine power axle the 29, two clutch coupling C2, the 2nd input shaft 2, second gear driving toothed gear 4, second gear follower gear 8, reverse gear synchronizer 9, back gear 10, reverse gear follower gear 18a, five grades of follower gear 18b, three or five grades of driving toothed gears 16, first input shaft 1, grade driving toothed gear 17, one grade of follower gear 12, one third gear synchronizer 13, first output shaft 5, first is main subtracts driving toothed gear 6, master subtracts follower gear 26, differential mechanism 25.
First alternative reverse gear runs drive path: engine power axle the 29, two clutch coupling C2, the 2nd input shaft 2, second gear driving toothed gear 4, second gear follower gear 8, reverse gear synchronizer 9, back gear 10, reverse gear follower gear 18a, five grades of follower gear 18b, three or five grades of driving toothed gears 16, third gear follower gear 11, one third gear synchronizer 13, first output shaft 5, first is main subtracts driving toothed gear 6, master subtracts follower gear 26, differential mechanism 25.
2nd alternative reverse gear runs drive path: engine power axle the 29, two clutch coupling C2, the 2nd input shaft 2, second gear driving toothed gear 4, second gear follower gear 8, reverse gear synchronizer 9, back gear 10, reverse gear follower gear 18a, five grades of follower gear 18b, five or seven grades of synchronizer the 21, two output shaft the 28, two masters subtract driving toothed gear 27, master subtracts follower gear 26, differential mechanism 25.
3rd alternative reverse gear runs drive path: engine power axle the 29, two clutch coupling C2, the 2nd input shaft 2, second gear driving toothed gear 4, second gear follower gear 8, reverse gear synchronizer 9, back gear 10, reverse gear follower gear 18a, five grades of follower gear 18b, three or five grades of driving toothed gears 16, first input shaft 1, seven grades driving toothed gear 19, seven grades of follower gears 20, five or seven grades of synchronizer the 21, two output shaft the 28, two masters subtract driving toothed gear 27, master subtracts follower gear 26, differential mechanism 25.
Preferred reverse gear scheme can realize bigger reverse gear speed ratio, and alternative reverse gear scheme can realize less reverse gear speed ratio, because expanding reverse gear vehicle speed range.
Below by reference to the accompanying drawings to invention has been exemplary description. Obviously; specific implementation of the present invention is not subject to the restrictions described above; as long as have employed the improvement of the various unsubstantialities that the design of the method for the present invention carries out with technical scheme; or without improving, the design of the present invention and technical scheme directly applied to other occasion, all within protection scope of the present invention.

Claims (11)

1. an automobile double clutch variator, comprises the first clutch coupling (C1), the 2nd clutch coupling (C2), the first input shaft (1), the 2nd input shaft (2), the first output shaft (5), the 2nd output shaft (28);
2nd input shaft (2) is tubular shaft, coaxially air-ground is enclosed within the first input shaft (1);
Engine power axle (29) is engaged by the first clutch coupling (C1) and the first input shaft (1) or is separated; Engine power axle (29) by the 2nd clutch coupling (C2) with the 2nd input shaft (2) engage or be separated;
First output shaft (5) is arranged in the both sides of the 2nd input shaft (2) parallelly with the 2nd output shaft (28);
Described the first input shaft (1) and the 2nd input shaft (2) are respectively equipped with multiple driving toothed gear being fastenedly connected with it, described the first output shaft (5) and the 2nd output shaft (28) are respectively equipped with the follower gear of multiple empty set on corresponding axle; Described follower gear engages with corresponding driving toothed gear;
Described the first output shaft (5) is provided with first and main subtracts driving toothed gear (6), and the first main driving toothed gear (6) that subtracts subtracts follower gear (26) with the master on differential mechanism (25) and engages; The 2nd described output shaft (28) is provided with the 2nd and main subtracts driving toothed gear (27), and the 2nd main driving toothed gear (27) that subtracts subtracts follower gear (26) and engages with described master;
Described the first output shaft (5) and the 2nd output shaft (28) are respectively equipped with for controlling joint and the advance shelves synchronizer being separated between described follower gear and the output shaft at its place;
It is characterized in that:
Also being provided with one to the intermeshing back gear pair for reverse gear on described the first output shaft (5) and the 2nd output shaft (28), two gears of described back gear pair are the floating gear of empty set on corresponding axle;
Back gear (10) is also provided with one for realizing the reverse gear synchronizer (9) of multiple reverse gear speed ratio.
2. according to automobile double clutch variator according to claim 1, it is characterised in that:
Described driving toothed gear comprises three or the five grades of driving toothed gears (16) being located on the first input shaft (1), one grade of driving toothed gear (17) and seven grades of driving toothed gears (19), and the six grades of driving toothed gears (3), second gear driving toothed gear (4) and the fourth gear driving toothed gear (15) that are located on the 2nd input shaft (2);
Described follower gear comprises the second gear follower gear (8), third gear follower gear (11) and the one grade of follower gear (12) that are located on the first output shaft (5), and the six grades of follower gears (24) being located on the 2nd output shaft (28), fourth gear follower gear (22), five grades of follower gears (18b) and seven grades of follower gears (20);
Described second gear follower gear (8) is engaged with second gear driving toothed gear (4); Third gear follower gear (11) engages with three or five grades of driving toothed gears (16); One grade of follower gear (12) is engaged with one grade of driving toothed gear (17);
Six grades of described follower gears (24) are engaged with six grades of driving toothed gears (3); Fourth gear follower gear (22) engages with fourth gear driving toothed gear (15); Five grades of follower gears (18b) are engaged with three or five grades of driving toothed gears (16); Seven grades of follower gears (20) are engaged with seven grades of driving toothed gears (19).
3. according to automobile double clutch variator according to claim 2, it is characterised in that: two gears of described back gear pair are respectively: the back gear (10) being located on the first output shaft (5) and the reverse gear follower gear (18a) being located on the 2nd output shaft (28).
4. according to automobile double clutch variator according to claim 3, it is characterised in that: described reverse gear follower gear (18a) and five grades of follower gears (18b) are coaxially fixed together.
5. according to automobile double clutch variator according to claim 2, it is characterised in that: described advance shelves synchronizer comprise be located on the first output shaft (5) for controlling the second gear synchronizer (7) that second gear follower gear (8) and the first output shaft (5) are separated and engage; Described second gear synchronizer (7) is arranged on described second gear follower gear (8) and master subtracts between driving toothed gear (6) or between described second gear follower gear (8) and back gear (10).
6. according to automobile double clutch variator according to claim 2, it is characterized in that: described reverse gear synchronizer (9) is arranged between described second gear follower gear (8) and back gear (10), for the joint that controls described second gear follower gear (8) and back gear (10) be separated.
7. according to automobile double clutch variator according to claim 2, it is characterized in that: described advance shelves synchronizer comprises and is located at that the first output shaft (5) is upper, for controlling the third gear synchronizer (13) that one grade of follower gear (12) and third gear follower gear (11) and the first output shaft (5) are separated and engage, a described third gear synchronizer (13) is arranged between described one grade follower gear (12) and third gear follower gear (11).
8. according to automobile double clutch variator according to claim 2, it is characterized in that: described advance shelves synchronizer comprises and is located at that the 2nd output shaft (28) is upper, for controlling four or six grades of synchronizers (23) that fourth gear follower gear (22) is separated with six grades of follower gears (24) and the 2nd output shaft (28) and engages, four or six grades of described synchronizers (23) are arranged between described fourth gear follower gear (22) and six grades of follower gears (24).
9. according to automobile double clutch variator according to claim 2, it is characterized in that: described advance shelves synchronizer comprises and is located at that the 2nd output shaft (28) is upper, for controlling between five grades of follower gears (18b) and seven grades of follower gears (20) and the 2nd output shaft (28) five or the seven grades of synchronizers (21) being separated and engaging, five or seven grades of described synchronizers (21) are arranged between described five grade follower gear (18b) and seven grades of follower gears (20).
10. according to automobile double clutch variator according to claim 2, it is characterised in that: the radial dimension of described one grade of follower gear (12), second gear follower gear (8), third gear follower gear (11), fourth gear follower gear (22), five grades of follower gears (18b), six grades of follower gears (24) and back gear (10) makes the sliding cover of corresponding synchronizer can partly embed in corresponding teeth portion.
11. according to automobile double clutch variator according to claim 1, it is characterised in that: described the first output shaft (5) or the 2nd output shaft (28) are provided with parking wheel (14) being fixedly connected with it.
CN201410127289.3A 2014-03-31 2014-03-31 A kind of automobile double clutch variator Active CN103836126B (en)

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PCT/CN2014/090495 WO2015149515A1 (en) 2014-03-31 2014-11-06 Automobile dual-clutch transmission

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CN103836126B (en) * 2014-03-31 2016-06-01 奇瑞汽车股份有限公司 A kind of automobile double clutch variator
CN208134080U (en) * 2016-12-21 2018-11-23 舍弗勒技术股份两合公司 driving device and motor vehicle
CN110617312B (en) * 2019-09-12 2021-08-31 何耀华 All-gear stepless automatic speed change and speed ratio active control system

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Application publication date: 20140604

Assignee: CHERY AUTOMOBILE CO., LTD.

Assignor: Saic Chery Automobile Co., Ltd.

Contract record no.: 2016990000241

Denomination of invention: Dual-clutch transmission of auto and speed change method thereof

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Record date: 20160620

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Address after: 241009 Changchun Road, Wuhu economic and Technological Development Zone, Anhui 8

Patentee after: Chery Holdings Limited

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Patentee before: Chery Holding Co., Ltd.