CN103836126A - Double-clutch transmission of car - Google Patents
Double-clutch transmission of car Download PDFInfo
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- CN103836126A CN103836126A CN201410127289.3A CN201410127289A CN103836126A CN 103836126 A CN103836126 A CN 103836126A CN 201410127289 A CN201410127289 A CN 201410127289A CN 103836126 A CN103836126 A CN 103836126A
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- 230000005540 biological transmission Effects 0.000 title abstract description 18
- 238000000034 method Methods 0.000 description 3
- 230000009977 dual effect Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed 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
- F16H3/085—Toothed 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 with more than one output shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed 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
- F16H3/12—Toothed 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 with means for synchronisation not incorporated in the clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed 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
- F16H3/087—Toothed 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
- F16H3/093—Toothed 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
- F16H2003/0931—Toothed 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a double-clutch transmission of a car. A first output shaft (5) and a second output shaft (28) are provided with a backward gear pair used for back action, two gears of the backward gear pair are mutually meshed and are floating gears arranged on the corresponding shafts in an empty sleeved mode, and the backward gear (10) on the first output shaft (5) is provided with a backward synchronizer (9) used for achieving a plurality of backward gear speed ratios. By means of the technical scheme, compared with the prior art, the double-clutch transmission of the car adopts the two output shafts, can achieve seven forward gears, at least one backward gear and an empty gear, and is high in backward gear speed. The double-clutch transmission of the car is short in axial distance, is reasonable in structural arrangement, and meets the requirements for being simple and compact.
Description
Technical field
The invention belongs to the technical field of automotive transmission.More particularly, the present invention relates to a kind of automobile double clutch speed changer.
Background technique
Dual-clutch transmission adopts double clutch construction and fixed axis gear transmission, with hydraulic automatic speed variator (AT, Automatic Transmission) and CVT (continuously variable transmission) (CVT, Continuously Variable Transmission) compare, its transmission efficiency is high, and oil consumption is low, has solved electric control mechanical type automatic speed variator (AMT simultaneously, Automated Manual Transmission) there is the shortcoming of power interruption, greatly improve driving comfortability.Therefore progressively become the focus of gearbox industry development.
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 driven gear, large diameter gear engages with second gear driving gear, and small-diameter gear engages with reverse gear, to realize reverse gear ratio.Obviously, the limited size of reverse gear is in the distance at the external diameter of the second input shaft and the center of the first output shaft, simultaneously the distance of the first output shaft and the second output shaft has also limited the speed ratio of intermeshing small-diameter gear and reverse gear on this diaxon, and reverse gear ratio (input speed/output speed) is less.
Summary of the invention
The invention provides a kind of automobile double clutch speed changer, only its objective is and realize multiple reverse gear ratios by two output shafts, and reverse gear ratio is larger, simultaneously its reasonable structural arrangement, simple, compact.
For achieving the above object, the present invention takes following technological scheme:
Automobile double clutch speed changer of the present invention, comprises first clutch, second clutch, the first input shaft, the second input shaft, the first output shaft, the second output shaft;
The second input shaft is hollow shaft, and empty set is on the first input shaft coaxially;
Engine power axle is engaged or separates with the first input shaft by first clutch; Engine power axle is engaged or separates with the second input shaft by second clutch;
The first output shaft and the second output shaft are arranged in the both sides of the second input shaft abreast;
On the first described input shaft and the second input shaft, be respectively equipped with multiple driving gears that are fastenedly connected with it, on the first described output shaft and the second output shaft, be respectively equipped with the driven gear of multiple empty sets on corresponding axis; Described driven gear engages with corresponding driving gear;
The first described output shaft is provided with the first main driving gear that subtracts, and the first main driving gear that subtracts subtracts driven gear with the master on differential mechanism and engages; The second described output shaft is provided with the second main driving gear that subtracts, and the second main driving gear that subtracts also subtracts driven gear with described master and engages;
On the first described output shaft and the second output shaft, be respectively equipped with for controlling between described driven gear and the output shaft at its place and engage and the forward gears synchronizer separating;
On the first described output shaft and the second output shaft, be also provided with a pair of intermeshing reverse gear pair for reverse gear, two gears of described reverse gear pair are the floating gear of empty set on corresponding axis;
The reverse drive gear being positioned on the first described output shaft is also provided with one for realizing the reversing-gear synchronizer of multiple reverse gear ratios.
Described driving gear comprises three or five grades of driving gears that are located on the first input shaft, one grade of driving gear and seven grades of driving gears, and is located at six grades of driving gears, second gear driving gear and the fourth gear driving gear on the second input shaft;
Described driven gear comprises the second gear driven gear, third gear driven gear and the first speed driven gear that are located on the first output shaft, and is located at six grades of driven gears, fourth gear driven gear, five grades of driven gears and seven grades of driven gears on the second output shaft;
Described second gear driven gear engages with second gear driving gear; Third gear driven gear engages with three or five grades of driving gears; First speed driven gear engages with one grade of driving gear;
Six grades of described driven gears engage with six grades of driving gears; Fourth gear driven gear engages with fourth gear driving gear; Five grades of driven gears engage with three or five grades of driving gears; Seven grades of driven gears engage with seven grades of driving gears.
Two gears of described reverse gear pair are respectively: be located at the reverse gear on the first output shaft and be located at the reverse gear driven gear on the second output shaft.
Described reverse gear driven gear and five grades of driven gears are coaxially fixed together.
Described forward gears synchronizer comprise be located on the first output shaft for controlling, second gear driven gear separates with the first output shaft and the second gear synchronizer of joint; Described second gear synchronizer is arranged on described second gear driven gear and main subtracting between driving gear or between described second gear driven gear and reverse gear.
Described reversing-gear synchronizer is arranged between described second gear driven gear and reverse gear, for the joint of controlling described second gear driven gear and reverse gear with separate.
Described forward gears synchronizer comprise be located on the first output shaft, for controlling, first speed driven gear separates with the first output shaft with third gear driven gear and a third gear synchronizer of joint, a described third gear synchronizer is arranged between described first speed driven gear and third gear driven gear
Described forward gears synchronizer comprise be located on the second output shaft, for controlling, fourth gear driven gear separates with the second output shaft with six grades of driven gears and four or six grades of synchronizers of joint, four or six grades of described synchronizers are arranged between described fourth gear driven gear and six grades of driven gears.
Described forward gears synchronizer comprise be located on the second output shaft, for controlling, five grades of driven gears separate with the second output shaft with seven grades of driven gears and five or seven grades of synchronizers of joint, five or seven grades of described synchronizers are arranged between described five grades of driven gears and seven grades of driven gears.
The radial dimension of described first speed driven gear, second gear driven gear, third gear driven gear, fourth gear driven gear, five grades of driven gears, six grades of driven gears and reverse gear can partly embed in corresponding tooth portion the sliding sleeve of corresponding synchronizer.
The first described output shaft or the second 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, can realize seven forward gearss, at least one reverse gear and a neutral gear, and reverse gear ratio is larger; Its axial distance is short, and reasonable structural arrangement has met simple, compact requirement.
Brief description of the drawings
Fig. 1 is the expansion schematic diagram of driving mechanism of the present invention;
Fig. 2 is the side schematic view of structure shown in Fig. 1.
In figure, be labeled as:
1, the first input shaft, 2, the second input shaft, 3, six grades of driving gears, 4, second gear driving gear, 5, the first output shaft (A1), 6, the first output shaft master subtracts driving gear, 7, second gear synchronizer (S2), 8, second gear driven gear, 9, reversing-gear synchronizer (SR), 10, reverse gear, 11, third gear driven gear, 12, first speed driven gear, 13, one third gear synchronizer (S13), 14, parking wheel, 15, fourth gear driving gear, 16, three or five grades of driving gears, 17, one grade of driving gear, 18, five reverse gear driven gears, 18a, reverse gear driven gear, 18b, five grades of driven gears, 19, seven grades of driving gears, 20, seven grades of driven gears, 21, five or seven grades of synchronizers (S57), 22, fourth gear driven gear, 23, four or six grades of synchronizers (S46), 24, six grades of driven gears, 25, differential mechanism, 26, master subtracts driven gear, 27, the second output shaft master subtracts driving gear, 28, the second output shaft (A2), 29, engine power axle, C1, first clutch, C2, second clutch, 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
Contrast accompanying drawing below, by the description to embodiment, the specific embodiment of the present invention is described in further detail, to help those skilled in the art to have more complete, accurate and deep understanding to inventive concept of the present invention, technological scheme.
As shown in Figure 1 and Figure 2, be a kind of automobile double clutch speed changer structure of the present invention.Specifically, be the seven speed dual clutch transmission for the horizontal forerunner's automobile of motor.This speed changer comprises two clutches, two transmission shafts, two live axles and a differential mechanism.Specifically comprise the first input shaft 1, the second input shaft 2; First clutch C1, second clutch C2; The first output shaft 5, the second output shaft 28, differential mechanism 25;
The second input shaft 2 is hollow shaft, and empty set is on the first input shaft 1 coaxially;
The first output shaft 5 and the second output shaft 28 are arranged in the both sides of the second input shaft 2 abreast;
In order to solve the problem that prior art exists and to overcome its defect, implementation structure connection and reasonable arrangement, simple, compact goal of the invention, the technological scheme that the present invention takes is:
As shown in Figure 1 and Figure 2, automobile double clutch speed changer of the present invention, on the first described input shaft 1 and the second input shaft 2, be respectively equipped with multiple driving gears that are fastenedly connected with it, on the first described output shaft 5 and the second output shaft 28, be respectively equipped with the driven gear of multiple empty sets on corresponding axis; Described driven gear engages with corresponding driving gear.
Described driving gear comprises three or the five grades of driving gears 16 that are located on the first input shaft 1, one grade of driving gear 17 and seven grades of driving gears 19, and is located at six grades of driving gears 3, second gear driving gear 4 and the fourth gear driving gear 15 on the second input shaft 2.
Described driven gear comprises the second gear driven gear 8, third gear driven gear 11 and the first speed driven gear 12 that are located on the first output shaft 5, and is located at six grades of driven gears 24 on the second output shaft 28, fourth gear driven gear 22, five grades of driven gear 18b and seven grades of driven gears 20;
Described second gear driven gear 8 engages with second gear driving gear 4; Third gear driven gear 11 engages with three or five grades of driving gears 16; First speed driven gear 12 engages with one grade of driving gear 17;
Six grades of described driven gears 24 engage with six grades of driving gears 3; Fourth gear driven gear 22 engages with fourth gear driving gear 15; Five grades of driven gear 18b engage with three or five grades of driving gears 16; Seven grades of driven gears 20 engage with seven grades of driving gears 19.
The the 3rd and the 5th grade of employing of speed changer shares driving gear, can shorten the axial distance of gearbox.
On the first described output shaft 5 and the second output shaft 28, be also provided with a pair of intermeshing reverse gear pair for reverse gear, two gears of described reverse gear pair are the floating gear of empty set on corresponding axis; Reverse gear pair is respectively: be located at the reverse gear 10 on the first output shaft 5 and be located at the reverse gear driven gear 18a on the second output shaft 28.
Described reverse gear driven gear 18a and five grades of driven gear 18b are coaxially fixed together.
The first described output shaft 5 multiplely engages and the forward gears synchronizer separating for the output shaft of controlling described driven gear and its place with being respectively equipped with on the second output shaft 28.
Described forward gears synchronizer comprise be located on the first output shaft 5, between second gear driven gear 8 and the first output shaft 5, separate and the second gear synchronizer 7 of joint for controlling.In a preferred embodiment, second gear synchronizer 7 is arranged on described second gear driven gear 8 and main subtracting between driving gear 6, and alternative embodiment is: described second gear synchronizer 7 is arranged between described second gear driven gear 8 and reverse gear 10.
Described forward gears synchronizer comprise be located on the first output shaft 5, for controlling, first speed driven gear 12 separates with the first output shaft 5 with third gear driven gear 11 and a third gear synchronizer 13 of joint; A described third gear synchronizer 13 is arranged between described first speed driven gear 12 and third gear driven gear 11.
Described forward gears synchronizer comprise be located on the second output shaft 28, for controlling, fourth gear driven gear 22 separates with the second output shaft 28 with six grades of driven gears 24 and four or six grades of synchronizers 23 of joint; Four or six grades of described synchronizers 23 are arranged between described fourth gear driven gear 22 and six grades of driven gears 24.
Described forward gears synchronizer comprise be located on the second output shaft 28, for controlling, five grades of driven gear 18b separate with the second output shaft 28 with seven grades of driven gears 20 and five or seven grades of synchronizers 21 of joint; Five or seven grades of described synchronizers 21 are arranged between described five grades of driven gear 18b and seven grades of driven gears 20.
Be positioned on the reverse drive gear 10 of the first output shaft 5 and be also provided with one for realizing the reversing-gear synchronizer 9 of multiple reverse gear ratios, engage and separate with reverse gear 10 for controlling described second gear driven gear 8, described reversing-gear synchronizer 9 is arranged between described second gear driven gear 8 and reverse gear 10.
The first described output shaft 5 or the second 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 when ensureing to hang P shelves.
For reducing axial length, the radial dimension of the free gear that major part on the first output shaft 5 and the second output shaft 28 is unsteady can be designed to enough large, and when meeting synchronizer joint, the sliding sleeve of synchronizer can partly embed gear inside.These free gears comprise second gear driven gear 8, reverse gear 10, third gear driven gear 11, first speed driven gear 12, five grades of driven gear 18b, fourth gear driven gear 22 and six grades of driven gears 24.
While hanging into D shelves, engage the synchronizer of the gear that advances, make the corresponding driven gear of the gear that advances and the output shaft at its place interconnected, then switch clutch obtains input torque,, by the clutch of suggestion and the combination of synchronizer, can realize seven forward gearss.
Realize in the following manner for one grade:
As shown in Figure 1, the sliding sleeve of a third gear synchronizer 13 moves to right, engage first clutch C1, by moment of torsion be passed to successively the first input shaft 1, one grade of driving gear 17, first speed driven gear 12, the first output shaft 5, first output shaft master subtract driving gear 6 and the main driven gear 26 that subtracts.Can realize the optimization of speed ratio by adjusting the size of each gear.
Similarly, other gear that advances is realized by engaging corresponding synchronizer and clutch.
While hanging into R shelves, except engaged reverse synchronizer 9, need engage the synchronizer of a certain odd gear simultaneously, at least can realize a reverse gear, preferably engage one grade of synchronizer, to obtain maximum reverse gear ratio.
Reverse gear realizes in the following manner:
Engaging clutch C2, is passed to the second input shaft 2, second gear driving gear 4, second gear driven gear 8 successively by moment of torsion; Engaged reverse synchronizer 9, reverse gear 10 and the synchronized rotation transmitting torque of second gear driven gear 8.Moment of torsion is delivered to reverse driving gear 10, then to reverse gear driven gear 18a, then to five grades of driven gear 18b.Now, the rotary speed direction of five grades of driven gear 18b is contrary when the forward gears with it, so far, specifically correspondingly can realize four reverse gear ratios in conjunction with different odd number shelves.
Preferred reverse gear mode of execution is as follows:
Moment of torsion is passed to three or five grades of driving gears 16, the first input shaft 1, one grade of driving gear 17 and first speed driven gear 12 successively by five grades of driven gear 18b; The move to right sliding sleeve of a third gear synchronizer 13, first speed driven gear 12 and the synchronized rotation of the first output shaft 5, transmitting torque to the first output shaft master subtracts driving gear 6, finally reaches the main driven gear 26 that subtracts.
This preferred version can obtain maximum reverse gear ratio, and without operation synchronizer, only input torque is switched to first clutch C1 by second clutch C2 and can realize one grade.The reverse gear ratio scope of the dual-clutch transmission in existing market is 14-18, and the reverse gear ratio of this scheme can reach more than 20.
Alternative reverse gear ratio can be realized by the synchronizer that engages other odd gear except a grade, uses third gear, five grades or seven grades of gear pair transmitting torques.
In sum, the concrete moment of torsion transfer route of each gear of the present invention is respectively:
One grade of operation: engine power axle 29, first clutch C1, the first 1, one grade of input shaft driving gear 17, the main driving gear 6 that subtracts of first speed driven gear 12, one third gear synchronizer 13, the first output shaft 5, the first, the main driven gear 26, differential mechanism 25 of subtracting.
Second gear operation: engine power axle 29, second clutch C2, the second input shaft 2, second gear driving gear 4, second gear driven gear 8, the main driving gear 6 that subtracts of second gear synchronizer 7, the first output shaft 5, the first, the main driven gear 26, differential mechanism 25 of subtracting.
Third gear operation: engine power axle 29, first clutch C1,1, three five grade of driving gear 16 of the first input shaft, the main driving gear 6 that subtracts of third gear driven gear 11, one third gear synchronizer 13, the first output shaft 5, the first, the main driven gear 26, differential mechanism 25 of subtracting.
Fourth gear operation: engine power axle 29, second clutch C2, the second input shaft 2, fourth gear driving gear 15, the main driving gear 27 that subtracts of 22, four six grades of synchronizers of fourth gear driven gear, 23, the second output shaft 28, the second, the main driven gear 26, differential mechanism 25 of subtracting.
Five grades of operations: engine power axle 29, first clutch C1,16, five grades of driven gear 18b of 1, three five grade of driving gear of the first input shaft, five or seven grades of main driving gears 27 that subtract of synchronizer 21, the second output shaft 28, the second, the main driven gear 26, differential mechanism 25 of subtracting.
Six grades of operations: engine power axle 29, second clutch C2, the main driving gear 27 that subtracts of 24, four six grades of synchronizers of 3, six grades of driven gears of 2, six grades of driving gears of the second input shaft, 23, the second output shaft 28, the second, the main driven gear 26, differential mechanism 25 of subtracting.
Seven grades of operations: engine power axle 29, first clutch C1, the main driving gear 27 that subtracts of 20, five seven grades of synchronizers of 19, seven grades of driven gears of the first 1, seven grade of input shaft driving gear, 21, the second output shaft 28, the second, the main driven gear 26, differential mechanism 25 of subtracting.
Preferred reverse gear operation drive path is: engine power axle 29, second clutch C2, the second input shaft 2, second gear driving gear 4, second gear driven gear 8, reversing-gear synchronizer 9, reverse gear 10, reverse gear driven gear 18a, five grades of driven gear 18b, three or five grades of driving gears 16, the first 1, one grade of input shaft driving gear 17, first speed driven gear 12, the main driving gear 6 that subtracts of one third gear synchronizer 13, the first output shaft 5, the first, the main driven gear 26, differential mechanism 25 of subtracting.
The first alternative reverse gear operation drive path is: engine power axle 29, second clutch C2, the second input shaft 2, second gear driving gear 4, second gear driven gear 8, reversing-gear synchronizer 9, reverse gear 10, reverse gear driven gear 18a, five grades of driven gear 18b, three or five grades of driving gears 16, third gear driven gear 11, the main driving gear 6 that subtracts of one third gear synchronizer 13, the first output shaft 5, the first, the main driven gear 26, differential mechanism 25 of subtracting.
The second alternative reverse gear operation drive path is: engine power axle 29, second clutch C2, the second input shaft 2, second gear driving gear 4, second gear driven gear 8, reversing-gear synchronizer 9, reverse gear 10, reverse gear driven gear 18a, five grades of driven gear 18b, five or seven grades of main driving gears 27 that subtract of synchronizer 21, the second output shaft 28, the second, the main driven gear 26, differential mechanism 25 of subtracting.
The 3rd alternative reverse gear operation drive path is: engine power axle 29, second clutch C2, the second input shaft 2, second gear driving gear 4, second gear driven gear 8, reversing-gear synchronizer 9, reverse gear 10, reverse gear driven gear 18a, five grades of driven gear 18b, three or five grades of driving gears 16,19, seven grades of driven gears 20 of the first 1, seven grade of input shaft driving gear, five or seven grades of main driving gears 27 that subtract of synchronizer 21, the second output shaft 28, the second, the main driven gear 26, differential mechanism 25 of subtracting.
Preferred reverse gear scheme can realize larger reverse gear ratio, and alternative reverse gear scheme can realize less reverse gear ratio, because expanded reverse gear vehicle speed range.
Below by reference to the accompanying drawings the present invention is exemplarily described.Obviously; specific implementation of the present invention is not subject to the restrictions described above; as long as adopted the improvement of the various unsubstantialities that method of the present invention design and technological scheme carry out; or without improving, design of the present invention and technological scheme are directly applied to other occasion, all within protection scope of the present invention.
Claims (11)
1. an automobile double clutch speed changer, comprises first clutch (C1), second clutch (C2), the first input shaft (1), the second input shaft (2), the first output shaft (5), the second output shaft (28);
The second input shaft (2) is hollow shaft, and empty set is on the first input shaft (1) coaxially;
Engine power axle (29) is engaged or separates with the first input shaft (1) by first clutch (C1); Engine power axle (29) is engaged or separates with the second input shaft (2) by second clutch (C2);
The first output shaft (5) and the second output shaft (28) are arranged in the both sides of the second input shaft (2) abreast;
On described the first input shaft (1) and the second input shaft (2), be respectively equipped with multiple driving gears that are fastenedly connected with it, on described the first output shaft (5) and the second output shaft (28), be respectively equipped with the driven gear of multiple empty sets on corresponding axis; Described driven gear engages with corresponding driving gear;
Described the first output shaft (5) is provided with the first main driving gear (6) that subtracts, and the first main driving gear (6) that subtracts subtracts driven gear (26) with the master on differential mechanism (25) and engages; Described the second output shaft (28) is provided with the second main driving gear (27) that subtracts, and the second main driving gear (27) that subtracts subtracts driven gear (26) with described master and engages;
On described the first output shaft (5) and the second output shaft (28), be respectively equipped with for controlling between described driven gear and the output shaft at its place and engage and the forward gears synchronizer separating;
It is characterized in that:
On described the first output shaft (5) and the second output shaft (28), be also provided with a pair of intermeshing reverse gear pair for reverse gear, two gears of described reverse gear pair are the floating gear of empty set on corresponding axis;
On reverse gear (10), be also provided with one for realizing the reversing-gear synchronizer (9) of multiple reverse gear ratios.
2. according to automobile double clutch speed changer claimed in claim 1, it is characterized in that:
Described driving gear comprises three or the five grades of driving gears (16), one grade of driving gear (17) and the seven grades of driving gears (19) that are located on the first input shaft (1), and is located at six grades of driving gears (3), second gear driving gear (4) and fourth gear driving gear (15) on the second input shaft (2);
Described driven gear comprises the second gear driven gear (8), third gear driven gear (11) and the first speed driven gear (12) that are located on the first output shaft (5), and is located at six grades of driven gears (24), fourth gear driven gear (22), five grades of driven gears (18b) and seven grades of driven gears (20) on the second output shaft (28);
Described second gear driven gear (8) engages with second gear driving gear (4); Third gear driven gear (11) engages with three or five grades of driving gears (16); First speed driven gear (12) engages with one grade of driving gear (17);
Described six grades of driven gears (24) engage with six grades of driving gears (3); Fourth gear driven gear (22) engages with fourth gear driving gear (15); Five grades of driven gears (18b) engage with three or five grades of driving gears (16); Seven grades of driven gears (20) engage with seven grades of driving gears (19).
3. according to automobile double clutch speed changer claimed in claim 2, it is characterized in that: two gears of described reverse gear pair are respectively: be located at the reverse gear (10) on the first output shaft (5) and be located at the reverse gear driven gear (18a) on the second output shaft (28).
4. according to automobile double clutch speed changer claimed in claim 3, it is characterized in that: described reverse gear driven gear (18a) and five grades of driven gears (18b) are coaxially fixed together.
5. according to automobile double clutch speed changer claimed in claim 2, it is characterized in that: described forward gears synchronizer comprises the second gear synchronizer (7) that separates and engage with the first output shaft (5) for controlling second gear driven gear (8) being located on the first output shaft (5); Described second gear synchronizer (7) is arranged on described second gear driven gear (8) and main subtracting between driving gear (6) or between described second gear driven gear (8) and reverse gear (10).
6. according to automobile double clutch speed changer claimed in claim 2, it is characterized in that: described reversing-gear synchronizer (9) is arranged between described second gear driven gear (8) and reverse gear (10), for the joint of the second gear driven gear (8) described in controlling and reverse gear (10) with separate.
7. according to automobile double clutch speed changer claimed in claim 2, it is characterized in that: described forward gears synchronizer comprises a third gear synchronizer (13) that is located on the first output shaft (5), separates and engage with third gear driven gear (11) for controlling first speed driven gear (12) with the first output shaft (5), a described third gear synchronizer (13) is arranged between described first speed driven gear (12) and third gear driven gear (11).
8. according to automobile double clutch speed changer claimed in claim 2, it is characterized in that: described forward gears synchronizer comprises four or the six grades of synchronizers (23) that are located on the second output shaft (28), separate and engage with six grades of driven gears (24) for controlling fourth gear driven gear (22) with the second output shaft (28), described four or six grades of synchronizers (23) are arranged between described fourth gear driven gear (22) and six grades of driven gears (24).
9. according to automobile double clutch speed changer claimed in claim 2, it is characterized in that: described forward gears synchronizer comprise be located at the second output shaft (28) upper, for controlling five or the seven grades of synchronizers (21) that separate and engage between five grades of driven gears (18b) and seven grades of driven gears (20) and the second output shaft (28), between five grades of driven gears (18b) and seven grades of driven gears (20) described in described five or seven grades of synchronizers (21) are arranged on.
10. according to automobile double clutch speed changer claimed in claim 2, it is characterized in that: the radial dimension of described first speed driven gear (12), second gear driven gear (8), third gear driven gear (11), fourth gear driven gear (22), five grades of driven gears (18b), six grades of driven gears (24) and reverse gear (10) can partly embed in corresponding tooth portion the sliding sleeve of corresponding synchronizer.
11. according to automobile double clutch speed changer claimed in claim 1, it is characterized in that: described the first output shaft (5) or the second output shaft (28) are provided with the parking wheel (14) being fixedly connected with it.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410127289.3A CN103836126B (en) | 2014-03-31 | 2014-03-31 | A kind of automobile double clutch variator |
| PCT/CN2014/090495 WO2015149515A1 (en) | 2014-03-31 | 2014-11-06 | Automobile dual-clutch transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410127289.3A CN103836126B (en) | 2014-03-31 | 2014-03-31 | A kind of automobile double clutch variator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103836126A true CN103836126A (en) | 2014-06-04 |
| CN103836126B CN103836126B (en) | 2016-06-01 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410127289.3A Active CN103836126B (en) | 2014-03-31 | 2014-03-31 | A kind of automobile double clutch variator |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN103836126B (en) |
| WO (1) | WO2015149515A1 (en) |
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| WO2015149515A1 (en) * | 2014-03-31 | 2015-10-08 | 奇瑞汽车股份有限公司 | Automobile dual-clutch transmission |
| CN109723769A (en) * | 2019-03-08 | 2019-05-07 | 重庆青山工业有限责任公司 | The two reduction gear of pure electric vehicle retarder |
| CN110099812A (en) * | 2016-12-21 | 2019-08-06 | 舍弗勒技术股份两合公司 | Driving device and motor vehicle |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2015149515A1 (en) | 2015-10-08 |
| CN103836126B (en) | 2016-06-01 |
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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 Granted publication date: 20160601 License type: Exclusive License Record date: 20160620 |
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Effective date of registration: 20160712 Address after: 241000 Wuhu economic and Technological Development Zone, Changchun Road, No. 8, No. Patentee after: Chery Holding Co., Ltd. Address before: 241009 Wuhu economic and Technological Development Zone, Anhui, No. 8 Changchun Road Patentee before: Saic Chery Automobile Co., Ltd. |
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Address after: 241009 Changchun Road, Wuhu economic and Technological Development Zone, Anhui 8 Patentee after: Chery Holdings Limited Address before: 241000 Changchun Road, Wuhu economic and Technological Development Zone, Anhui 8 Patentee before: Chery Holding Co., Ltd. |