CN203926635U - Seven speed dual clutch formula automatic transmission - Google Patents
Seven speed dual clutch formula automatic transmission Download PDFInfo
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- CN203926635U CN203926635U CN201420358500.8U CN201420358500U CN203926635U CN 203926635 U CN203926635 U CN 203926635U CN 201420358500 U CN201420358500 U CN 201420358500U CN 203926635 U CN203926635 U CN 203926635U
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Abstract
A seven speed dual clutch formula automatic transmission, comprises the input shaft of two nested arrangement, two output shafts, an input countershaft, idle pulley supporting axle in the middle of one, a reverse gear shaft, this automatic transmission has seven forward gears and a reverse gear, two, four, six, the driving gear of seven grades is arranged on input one axle, and one, three, five, the driving gear of reverse gear is arranged on input countershaft, and two, four, six, the driven gear of seven grades is arranged on output one axle, and one, three, five, the driven gear of reverse gear is arranged on output two axles, on middle idle pulley supporting axle, empty set is provided with middle idle pulley, by middle idle pulley, engine power is delivered to input countershaft from inputting two axles, by input countershaft, be delivered to again on part gear, the driving gear of this part gear is arranged on input countershaft, thereby the driving gear of all gears is without being arranged in successively on two input shafts, has greatly shortened the axial length of whole speed changer, make overall structure compacter, arrangement is more reasonable.
Description
Technical field
The utility model relates to the speed changer technical field of automobile, relates in particular to a kind of seven speed dual clutch formula automatic transmission.
Background technique
Double-clutch automatic transmission is that two gearboxes and two clutches are integrated in a gearbox, two input shafts that connect together are rotationally connected with one of them clutch respectively, two input shafts transmit respectively the power of two gearbox speed groups, thereby by automatically switching and complete gearshift program between two clutches, therefore can realize the power shfit of gearshift procedure, at gearshift procedure, interrupt power, overcome the shortcoming of AMT shifting shock, vehicle is in gearshift procedure, the power of motor can be delivered to wheel all the time, gear shift is steady rapidly, not only guaranteed the acceleration of vehicle, and because vehicle no longer produces the abrupt deceleration situation causing due to gear shift, also improved greatly the travelling comfort of vehicle operating.
In existing double-clutch automatic transmission, the driving gear of all gears is to be arranged in successively on the first input shaft and the second input shaft, therefore the axial dimension of speed changer is longer, so for front transverse engine, the such vehicle of front-wheel drive, compact car particularly, because installing space is restricted, above-mentioned speed changer is more difficult employing just.Secondly, when part gear adopts while sharing driving gear, although can relatively reduce the axial dimension of speed changer, gear-driven speed ratio error may be larger, more difficultly realizes required speed ratio, is unfavorable for making motor in best region work.In addition, existing speed changer, because the gear of speed change is less, mostly generally is most six grades, and the more difficult reasonable distribution that realizes velocity ratio makes the more difficult optimum working zone that is operated in of motor, thereby the power character of car load and Economy are had a negative impact.
Model utility content
In view of this, be necessary to provide a kind of seven speed dual clutch formula automatic transmission, the axial length that it can shorten speed changer, makes actual speed ratio can more approach needed speed ratio, velocity ratio is distributed more reasonable.
Embodiment of the present utility model provides a kind of seven speed dual clutch formula automatic transmission, comprising:
Input one axle of mutually nested setting and input two axles, this is inputted on an axle second gear driving gear, fourth gear driving gear, six grades of driving gears and seven grades of driving gears is installed successively from one end, and this is inputted on two axles and is installed with and inputs two axle driving gears;
First clutch, this first clutch is inputted an axle with this and is connected;
Second clutch, this second clutch is inputted two axles with this and is connected;
Export an axle, this is exported the first final gear, second gear driven gear, fourth gear driven gear, six grades of driven gears and seven grades of driven gears is installed successively on an axle from one end;
Export two axles, this is exported first speed driven gear, reverse gear driven gear, the second final gear, five grades of driven gears and third gear driven gear is installed successively on two axles from one end;
Input countershaft is provided with successively one grade of driving gear, reverse driving gear, input countershaft actuation gear, five grades of driving gears and third speed drive gear from one end on this input countershaft, this input countershaft actuation gear is fixed on this input countershaft;
Middle idle pulley supporting axle, on this centre idle pulley supporting axle, empty set is provided with middle idle pulley;
Reverse gear shaft, on this reverse gear shaft, empty set is provided with reverse idler gear, wherein, this grade of driving gear and this first speed driven gear often mesh, this second gear driving gear and this second gear driven gear often mesh, this third speed drive gear and this third gear driven gear often mesh, this fourth gear driving gear and this fourth gear driven gear often mesh, these five grades of driving gears and this five grades of driven gears often mesh, these six grades of driving gears and this six grades of driven gears often mesh, these seven grades of driving gears and this seven grades of driven gears often mesh, this reverse driving gear and this reverse idler gear often mesh, this reverse idler gear and this reverse gear driven gear often mesh, this inputs two axle driving gears and this centre idle pulley often meshes, this centre idle pulley and this input countershaft actuation gear often mesh,
One reversing-gear synchronizer, the joint of this grade of reversing-gear synchronizer control and reverse gear;
Two fourth gear synchronizers, this two fourth gear synchronizer is controlled the joint of second gear and fourth gear;
Three Five-gear synchronizers, this three Five-gear synchronizer is controlled the joint of third gear and five grades; And
Six or seven grades of synchronizers, these six or seven grades of synchronizers are controlled the joint of six grades and seven grades.
Further, this grade of driving gear and this reverse driving gear are fixed on this input countershaft, this first speed driven gear and this reverse gear driven gear empty set are exported on two axles at this, and this reversing-gear synchronizer is arranged on this and exports on two axles and between this first speed driven gear and this reverse gear driven gear.
Further, this second gear driving gear and this fourth gear driving gear are fixed on this and input on an axle, this second gear driven gear and this fourth gear driven gear empty set are exported on an axle at this, and this two fourth gear synchronizer is arranged on this and exports on an axle and between this second gear driven gear and this fourth gear driven gear.
Further, this third speed drive gear and these five grades of driving gear empty sets are on this input countershaft, this third gear driven gear and these five grades of driven gears are fixed on this and export on two axles, and this three Five-gear synchronizer is arranged on this input countershaft and between this third speed drive gear and this five grades of driving gears.
Further, this third speed drive gear and these five grades of driving gears are fixed on this input countershaft, this third gear driven gear and these five grades of driven gear empty sets are exported on two axles at this, and this three Five-gear synchronizer is arranged on this and exports on two axles and between this third gear driven gear and this five grades of driven gears.
Further, these six grades of driving gears and these seven grades of driving gears are fixed on this and input on an axle, these six grades of driven gears and these seven grades of driven gear empty sets are exported on an axle at this, and these six or seven grades of synchronizers are arranged on this and export on an axle and between these six grades of driven gears and this seven grades of driven gears.
Further, these six grades of driving gears and these seven grades of driving gear empty sets are inputted on an axle at this, these six grades of driven gears and these seven grades of driven gears are fixed on this and export on an axle, and these six or seven grades of synchronizers are arranged on this and input on an axle and between these six grades of driving gears and this seven grades of driving gears.
Further, this seven speed dual clutch formula automatic transmission also comprises differential mechanism gear ring, this first final gear is fixed on this and exports on an axle, this second final gear is fixed on this and exports on two axles, and this first final gear and this second final gear often mesh with this differential mechanism gear ring simultaneously.
Further, this is inputted two axle driving gears, this centre idle pulley and this input countershaft actuation gear and forms the first co-planar gear set, this first final gear, this second final gear and this differential mechanism gear ring form the second co-planar gear set, this reverse driving gear, this reverse idler gear and this reverse gear driven gear form the 3rd co-planar gear set, wherein this first co-planar gear set is positioned at a wherein side of this second co-planar gear set, and the 3rd co-planar gear set is positioned at the opposite side of this second co-planar gear set.
Further, this inputs two axles is hollow shaft, and this is inputted two axles and is nested in this and inputs on an axle and to input an axle coaxial with this.
The beneficial effect that the technological scheme that embodiment of the present utility model provides is brought is:
(1) by a middle idle pulley, engine power is delivered to input countershaft from inputting two axles, then by input countershaft, be delivered to again on part gear (, three, five, reverse gear), the driving gear of this part gear is arranged on input countershaft, thereby the driving gear of all gears is without being arranged in successively on input one axle and input two axles, greatly shortened the axial length of whole speed changer, made the overall structure of speed changer more compact, arrangement is more reasonable.
(2) driving gear of each gear is by adopting the mode of non-shared driving gear often to mesh with corresponding driven gear, be that the driving gear of each gear is only as the driving gear of this gear, and be not re-used as the driving gear of another gear, all gears all do not adopt the mode that shares driving gear, make actual speed ratio can more approach needed speed ratio, improve power character and the Economy of car load;
(3) because entire length size obviously shortens, therefore under the prerequisite with common five, identical external dimension of six-speed gearbox, seven forward gearss can be set, thereby make gear range become large, it is more reasonable that velocity ratio distributes, and then obviously improve power performance and the car load class of car load.
Accompanying drawing explanation
Fig. 1 is the structural representation of the utility model the first embodiment's seven speed dual clutch formula automatic transmission.
Fig. 2 is the structural representation of the utility model the second embodiment's seven speed dual clutch formula automatic transmission.
Embodiment
The utility model provides a kind of seven speed dual clutch formula automatic transmission, a kind of seven speed dual clutch formula automatic transmission that is suitable for front transverse engine, forerunner's car particularly, the problems such as axial length for existing double-clutch automatic transmission is excessive, gear number is few, provide the seven speed dual clutch formula automatic transmission that a kind of axial length is little, ratio coverage is large, speed ratio easily distributes.For making the purpose of this utility model, technological scheme and advantage clearer, below in conjunction with accompanying drawing, the utility model mode of execution is further described.
The first embodiment
Fig. 1 is the structural representation of the utility model the first embodiment's seven speed dual clutch formula automatic transmission, please refer to the drawing 1, and the automatic transmission of the present embodiment comprises: one grade of driving gear 1, first speed driven gear 2, one reversing-gear synchronizer 3, reverse driving gear 4, reverse gear driven gear 5, the second final gear 6, input countershaft actuation gear 7, five grades of driven gears 8, five grades of driving gears 9, three Five-gear synchronizers 10, third gear driven gear 11, export two axles 12, third speed drive gear 13, input countershaft 14, middle idle pulley 15, second gear driving gear 16, fourth gear driving gear 17, input an axle 18, six grades of driving gears 19, seven grades of driving gears 20, six or seven grades of synchronizers 21, seven grades of driven gears 22, export an axle 23, six grades of driven gears 24, fourth gear driven gear 25, two fourth gear synchronizers 26, second gear driven gear 27, differential mechanism 28, differential mechanism gear ring 29, the first final gear 30, input two axle driving gears 31, engine crankshaft 32, first clutch 33, second clutch 34, input two axles 35, middle idle pulley supporting axle 36, reverse idler gear 37, and reverse gear shaft 38.
This automatic transmission comprises seven axles, is respectively: input one axle 18, input two axles 35, output one axle 23, output two axles 12, input countershaft 14, middle idle pulley supporting axle 36 and 38, seven axles of reverse gear shaft layout that is parallel to each other.Input on an axle 18 from second gear driving gear 16, fourth gear driving gear 17, six grades of driving gears 19 and seven grades of driving gears 20 are installed successively near motor one end.Input on two axles 35 and be installed with and input two axle driving gears 31.Export on an axle 23 from the first final gear 30, second gear driven gear 27, fourth gear driven gear 25, six grades of driven gears 24 and seven grades of driven gears 22 are installed successively near motor one end.Export on two axles 12 from first speed driven gear 2, reverse gear driven gear 5, the second final gear 6, five grades of driven gears 8 and third gear driven gears 11 are installed successively near motor one end.On input countershaft 14, from one grade of driving gear 1, reverse driving gear 4, input countershaft actuation gear 7, five grades of driving gears 9 and third speed drive gears 13 are installed successively near motor one end, input countershaft actuation gear 7 is fixed on input countershaft 14.On middle idle pulley supporting axle 36, empty set is provided with middle idle pulley 15.On reverse gear shaft 38, empty set is provided with reverse idler gear 37.
Input an axle 18 and input two axles 35 mutually nested setting, in the present embodiment, input two axles 35 be hollow shaft, and input two axles 35 are nested on input one axle 18 and with to input an axle 18 coaxial.First clutch 33 is connected and for control inputs one axle 18 with input one axle 18, second clutch 34 with input that two axles 35 are connected and for control inputs two axles 35.
One grade of driving gear 1 often meshes with first speed driven gear 2; Second gear driving gear 16 often meshes with second gear driven gear 27; Third speed drive gear 13 often meshes with third gear driven gear 11; Fourth gear driving gear 17 often meshes with fourth gear driven gear 25; Five grades of driving gears 9 and five grades of driven gears 8 often mesh; Six grades of driving gears 19 and six grades of driven gears 24 often mesh; Seven grades of driving gears 20 and seven grades of driven gears 22 often mesh; Reverse driving gear 4 often meshes with reverse idler gear 37, reverse idler gear 37 often meshes with reverse gear driven gear 5, be there is no direct meshing relation between reverse driving gear 4 and reverse gear driven gear 5, reverse gear driven gear 5 is by reverse idler gear 37 and reverse driving gear 4 engagement indirectly; Input two axle driving gears 31 and often mesh with middle idle pulley 15, middle idle pulley 15 and the 7 often engagements of input countershaft actuation gear.
Input two axle driving gears 31, middle idle pulley 15 and input countershaft actuation gear 7 and form the first co-planar gear set.The first final gear 30 is fixed on output one axle 23.The second final gear 6 is fixed on output two axles 12, the first final gear 30 and the second final gear 6 often mesh with differential mechanism gear ring 29 simultaneously, and the first final gear 30, the second final gear 6 and differential mechanism gear ring 29 form the second co-planar gear set.Reverse driving gear 4, reverse idler gear 37 and reverse gear driven gear 5 form the 3rd co-planar gear set.Wherein, the first co-planar gear set is positioned at the left side of the second co-planar gear set, and the 3rd co-planar gear set is positioned at the right side of the second co-planar gear set.
One grade of driving gear 1 and reverse driving gear 4 are fixed on input countershaft 14, first speed driven gear 2 and reverse gear driven gear 5 empty sets are on output two axles 12, one reversing-gear synchronizer 3 is arranged on output two axles 12 and between first speed driven gear 2 and reverse gear driven gear 5, is controlled and is engaged for one grade with reverse gear by a reversing-gear synchronizer 3.
Second gear driving gear 16 and fourth gear driving gear 17 are fixed on input one axle 18, second gear driven gear 27 and fourth gear driven gear 25 empty sets are on output one axle 23, two fourth gear synchronizers 26 are arranged on output one axle 23 and between second gear driven gear 27 and fourth gear driven gear 25, and second gear is controlled and engaged by two fourth gear synchronizers 26 with fourth gear.
In the present embodiment, third speed drive gear 13 and five grades of driving gear 9 empty sets are on input countershaft 14, third gear driven gear 11 and five grades of driven gears 8 are fixed on output two axles 12, three Five-gear synchronizers 10 are arranged on input countershaft 14 and between third speed drive gear 13 and five grades of driving gears 9, and third gear is controlled and engaged by three Five-gear synchronizers 10 with five grades.
In the present embodiment, six grades of driving gears 19 and seven grades of driving gears 20 are fixed on input one axle 18, six grades of driven gears 24 and seven grades of driven gear 22 empty sets are on output one axle 23, six or seven grades of synchronizers 21 are arranged on output one axle 23 and between six grades of driven gears 24 and seven grades of driven gears 22, are controlled and are engaged for six grades with seven grades by six or seven grades of synchronizers 21.
The automatic transmission of the present embodiment each grade of power transmission when work is as follows:
One grade of power transmission line a: reversing-gear synchronizer 3 and first speed driven gear 2 engage, second clutch 34 closures, Engine torque passes to input two axles 35 by second clutch 34, via input two axle driving gears 31, middle idle pulley 15, input countershaft actuation gear 7, pass to input countershaft 14 and one grade of driving gear 1, joint by first speed driven gear 2 and a reversing-gear synchronizer 3 transfers torque to the second final gear 6 on output two axles 12 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Second gear power transmission route: two fourth gear synchronizers 26 and second gear driven gear 27 engage, first clutch 33 closures, Engine torque passes to input one axle 18 by first clutch 33, via second gear driving gear 16, pass to second gear driven gear 27, by second gear driven gear 27 and engaging of two fourth gear synchronizers 26, transfer torque to the first final gear 30 on output one axle 23 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Third gear power transmission line: three Five-gear synchronizers 10 and third speed drive gear 13 engage, second clutch 34 closures, Engine torque passes to input two axles 35 by second clutch 34, via input two axle driving gears 31, middle idle pulley 15, input countershaft actuation gear 7 passes on input countershaft 14, joint by third speed drive gear 13 and three Five-gear synchronizers 10 transfers torque on third gear driven gear 11 again, by third gear driven gear 11, be delivered to the second final gear 6 on output two axles 12, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Fourth gear power transmission route: two fourth gear synchronizers 26 and fourth gear driven gear 25 engage, first clutch 33 closures, Engine torque passes to input one axle 18 by first clutch 33, via fourth gear driving gear 17, pass to fourth gear driven gear 25, by fourth gear driven gear 25 and engaging of two fourth gear synchronizers 26, transfer torque to the first final gear 30 on output one axle 23 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Five grades of power transmission lines: three Five-gear synchronizers 10 and five grades of driving gears 9 engage, second clutch 34 closures, Engine torque passes to input two axles 35 by second clutch 34, via input two axle driving gears 31, middle idle pulley 15, input countershaft actuation gear 7 passes on input countershaft 14, joint by five grades of driving gears 9 and three Five-gear synchronizers 10 transfers torque on five grades of driven gears 8 again, by five grades of driven gears 8, be delivered to the second final gear 6 on output two axles 12, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Six grades of power transmission routes: six or seven grades of synchronizers 21 and six grades of driven gears 24 engage, first clutch 33 closures, Engine torque passes to input one axle 18 by first clutch 33, via six grades of driving gears 19, pass to six grades of driven gears 24, by six grades of driven gears 24 and engaging of six or seven grades of synchronizers 21, transfer torque to the first final gear 30 on output one axle 23 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Seven grades of power transmission routes: six or seven grades of synchronizers 21 and seven grades of driven gears 22 engage, first clutch 33 closures, Engine torque passes to input one axle 18 by first clutch 33, via seven grades of driving gears 20, pass to seven grades of driven gears 22, by seven grades of driven gears 22 and engaging of six or seven grades of synchronizers 21, transfer torque to the first final gear 30 on output one axle 23 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Reverse gear power transmission line a: reversing-gear synchronizer 3 and reverse gear driven gear 5 engage, second clutch 34 closures, Engine torque passes to input two axles 35 by second clutch 34, via input two axle driving gears 31, middle idle pulley 15, input countershaft actuation gear 7 passes to input countershaft 14 and reverse driving gear 4, through reverse idler gear 37, power is passed on reverse gear driven gear 5, by a reversing-gear synchronizer 3 and engaging of reverse gear driven gear 5, transfer torque to the second final gear 6 on output two axles 12 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
One grade is changed second gear process: in the time of one grade, a reversing-gear synchronizer 3 and first speed driven gear 2 engage, second clutch 34 closures, and first clutch 33 is opened; Dual-clutch transmission control system is sent one grade and is changed after second gear instruction, gear shifting actuating mechanism engages two fourth gear synchronizers 26 and second gear driven gear 27 in advance, now first clutch 33 is still in open mode, i.e. first clutch 33 and input one axle 18 transferring power not; Along with shift process continues, second clutch 34 is opened gradually, and meanwhile first clutch 33 is closed gradually, in this process, has all the time clutch to engage, and there will not be torque break; Second clutch 34 is opened completely, after the complete closure of first clutch 33, shift process finishes.Gear is now second gear, and second clutch 34 is in open mode, i.e. second clutch 34, input two axles 35 transferring power not, and engine power is delivered on second gear driven gear 27 via first clutch 33.In like manner, those skilled in the art are according to the schedule of double-clutch automatic transmission for shift process between all the other gears of the present embodiment, can draw the shift process between all the other gears of the present embodiment, do not repeat them here.
The second embodiment
Fig. 2 is the structural representation of the utility model the second embodiment's seven speed dual clutch formula automatic transmission, please refer to the drawing 2, the difference of the automatic transmission of the present embodiment and the first embodiment's automatic transmission is: in the present embodiment, third gear driven gear 11 and five grades of driven gear 8 empty sets are on output two axles 12, third speed drive gear 13 and five grades of driving gears 9 are fixed on input countershaft 14, and three Five-gear synchronizers 10 are arranged on output two axles 12 and between third gear driven gear 11 and five grades of driven gears 8; Six grades of driving gears 19 and seven grades of driving gear 20 empty sets are on input one axle 18, six grades of driven gears 24 and seven grades of driven gears 22 are fixed on output one axle 23, and six or seven grades of synchronizers 21 are arranged on input one axle 18 and between six grades of driving gears 19 and seven grades of driving gears 20.Other structures and working principle about the present embodiment can, with reference to above-mentioned the first embodiment, not repeat them here.
It is also understood that ground, in the 3rd embodiment of the present utility model, can also be: third speed drive gear 13 and five grades of driving gear 9 empty sets are on input countershaft 14, third gear driven gear 11 and five grades of driven gears 8 are fixed on output two axles 12, and three Five-gear synchronizers 10 are arranged on input countershaft 14 and between third speed drive gear 13 and five grades of driving gears 9; Six grades of driving gears 19 and seven grades of driving gear 20 empty sets are on input one axle 18, six grades of driven gears 24 and seven grades of driven gears 22 are fixed on output one axle 23, and six or seven grades of synchronizers 21 are arranged on input one axle 18 and between six grades of driving gears 19 and seven grades of driving gears 20.Other structures and working principle about the present embodiment can, with reference to above-mentioned the first embodiment, not repeat them here.
It is also understood that ground, in the 4th embodiment of the present utility model, can also be: third gear driven gear 11 and five grades of driven gear 8 empty sets are on output two axles 12, third speed drive gear 13 and five grades of driving gears 9 are fixed on input countershaft 14, and three Five-gear synchronizers 10 are arranged on output two axles 12 and between third gear driven gear 11 and five grades of driven gears 8; Six grades of driving gears 19 and seven grades of driving gears 20 are fixed on input one axle 18, six grades of driven gears 24 and seven grades of driven gear 22 empty sets are on output one axle 23, and six or seven grades of synchronizers 21 are arranged on output one axle 23 and between six grades of driven gears 24 and seven grades of driven gears 22.Other structures and working principle about the present embodiment can, with reference to above-mentioned the first embodiment, not repeat them here.
The utility model embodiment's double-clutch automatic transmission comprises two coaxially arranged input shafts, two output shafts, an input countershaft, idle pulley supporting axle in the middle of one, a reverse gear shaft, this automatic transmission has seven forward gears and a reverse gear, two, four, six, the driving gear of seven grades is arranged on input one axle, one, three, five, the driving gear of reverse gear is arranged on input countershaft, two, four, six, the driven gear of seven grades is arranged on output one axle, one, three, five, the driven gear of reverse gear is arranged on output two axles, on middle idle pulley supporting axle, empty set is provided with middle idle pulley.The seven speed dual clutch formula automatic transmission of the present embodiment has following beneficial effect:
(1) by a middle idle pulley, engine power is delivered to input countershaft from inputting two axles, then by input countershaft, be delivered to again on part gear (, three, five, reverse gear), the driving gear of this part gear is arranged on input countershaft, thereby the driving gear of all gears is without being arranged in successively on input one axle and input two axles, greatly shortened the axial length of whole speed changer, made the overall structure of speed changer more compact, arrangement is more reasonable.
(2) driving gear of each gear is by adopting the mode of non-shared driving gear often to mesh with corresponding driven gear, be that the driving gear of each gear is only as the driving gear of this gear, and be not re-used as the driving gear of another gear, all gears all do not adopt the mode that shares driving gear, make actual speed ratio can more approach needed speed ratio, improve power character and the Economy of car load;
(3) because entire length size obviously shortens, therefore under the prerequisite with common five, identical external dimension of six-speed gearbox, seven forward gearss can be set, thereby make gear range become large, it is more reasonable that velocity ratio distributes, and then obviously improve power performance and the car load class of car load.
In this article, term " comprises ", " comprising " or its any other variant are intended to contain comprising of nonexcludability, except comprising those listed key elements, but also can comprise other key elements of clearly not listing.
In this article, the related noun of locality such as forward and backward, upper and lower is to be arranged in figure and component position each other defines with component in accompanying drawing, just clear and convenient for expression technology scheme.The use that should be appreciated that the described noun of locality should not limit the scope that the application asks for protection.
In the situation that not conflicting, the feature in above-described embodiment and embodiment can mutually combine herein.
The foregoing is only preferred embodiment of the present utility model, not in order to limit the utility model, all within spirit of the present utility model and principle, any modification of doing, be equal to replacement, improvement etc., within all should being included in protection domain of the present utility model.
Claims (10)
1. a seven speed dual clutch formula automatic transmission, is characterized in that, comprising:
Input one axle (18) of mutually nested setting and input two axles (35), this inputs upper second gear driving gear (16), fourth gear driving gear (17), six grades of driving gears (19) and the seven grades of driving gears (20) of being provided with successively from one end of an axle (18), and this is inputted on two axles (35) and is installed with and inputs two axle driving gears (31);
First clutch (33), this first clutch (33) is inputted an axle (18) with this and is connected;
Second clutch (34), this second clutch (34) is inputted two axles (35) with this and is connected;
Export an axle (23), this exports upper the first final gear (30), second gear driven gear (27), fourth gear driven gear (25), six grades of driven gears (24) and the seven grades of driven gears (22) of being provided with successively from one end of an axle (23);
Export two axles (12), this exports upper first speed driven gear (2), reverse gear driven gear (5), the second final gear (6), five grades of driven gears (8) and the third gear driven gear (11) of being provided with successively from one end of two axles (12);
Input countershaft (14), upper one grade of driving gear (1), reverse driving gear (4), input countershaft actuation gear (7), five grades of driving gears (9) and the third speed drive gear (13) of being provided with successively from one end of this input countershaft (14), this input countershaft actuation gear (7) is fixed on this input countershaft (14);
Middle idle pulley supporting axle (36), idle pulley (15) in the middle of the upper empty set of this centre idle pulley supporting axle (36) is provided with;
Reverse gear shaft (38), the upper empty set of this reverse gear shaft (38) is provided with reverse idler gear (37), wherein, this one grade of driving gear (1) often meshes with this first speed driven gear (2), this second gear driving gear (16) often meshes with this second gear driven gear (27), this third speed drive gear (13) often meshes with this third gear driven gear (11), this fourth gear driving gear (17) often meshes with this fourth gear driven gear (25), these five grades of driving gears (9) often mesh with these five grades of driven gears (8), these six grades of driving gears (19) often mesh with these six grades of driven gears (24), these seven grades of driving gears (20) often mesh with these seven grades of driven gears (22), this reverse driving gear (4) often meshes with this reverse idler gear (37), this reverse idler gear (37) often meshes with this reverse gear driven gear (5), this is inputted two axle driving gears (31) and often meshes with this centre idle pulley (15), this centre idle pulley (15) often meshes with this input countershaft actuation gear (7),
One reversing-gear synchronizer (3), the joint of this grade of reversing-gear synchronizer (3) control and reverse gear;
Two fourth gear synchronizers (26), this two fourth gear synchronizer (26) is controlled the joint of second gear and fourth gear;
Three Five-gear synchronizers (10), this three Five-gear synchronizer (10) is controlled the joint of third gear and five grades; And
Six or seven grades of synchronizers (21), this six or seven grades of synchronizers (21) are controlled the joint of six grades and seven grades.
2. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this one grade of driving gear (1) and this reverse driving gear (4) are fixed on this input countershaft (14), it is upper that this first speed driven gear (2) and this reverse gear driven gear (5) empty set are exported two axles (12) at this, and this reversing-gear synchronizer (3) is arranged on this and exports two axles (12) above and be positioned between this first speed driven gear (2) and this reverse gear driven gear (5).
3. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this second gear driving gear (16) and this fourth gear driving gear (17) are fixed on this and input on an axle (18), it is upper that this second gear driven gear (27) and this fourth gear driven gear (25) empty set are exported an axle (23) at this, and this two fourth gear synchronizer (26) is arranged on this and exports an axle (23) above and be positioned between this second gear driven gear (27) and this fourth gear driven gear (25).
4. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this third speed drive gear (13) and this five grades of driving gears (9) empty set are inputted on countershaft (14) at this, this third gear driven gear (11) and this five grades of driven gears (8) are fixed on this and export two axles (12) above, and this three Five-gear synchronizer (10) is arranged on this input countershaft (14) above and is positioned between this third speed drive gear (13) and this five grades of driving gears (9).
5. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this third speed drive gear (13) and this five grades of driving gears (9) are fixed on this input countershaft (14), it is upper that this third gear driven gear (11) and this five grades of driven gears (8) empty set are exported two axles (12) at this, and this three Five-gear synchronizer (10) is arranged on this and exports two axles (12) above and be positioned between this third gear driven gear (11) and this five grades of driven gears (8).
6. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: these six grades of driving gears (19) and this seven grades of driving gears (20) are fixed on this and input on an axle (18), it is upper that these six grades of driven gears (24) and this seven grades of driven gears (22) empty set are exported an axle (23) at this, and these six or seven grades of synchronizers (21) are arranged on this and export an axle (23) above and be positioned between these six grades of driven gears (24) and this seven grades of driven gears (22).
7. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: these six grades of driving gears (19) and this seven grades of driving gears (20) empty set are inputted on an axle (18) at this, these six grades of driven gears (24) and this seven grades of driven gears (22) are fixed on this and export an axle (23) above, and these six or seven grades of synchronizers (21) are arranged on this and input an axle (18) above and be positioned between these six grades of driving gears (19) and this seven grades of driving gears (20).
8. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this automatic transmission also comprises differential mechanism gear ring (29), this first final gear (30) is fixed on this and exports on an axle (23), this second final gear (6) is fixed on this and exports two axles (12) above, and this first final gear (30) and this second final gear (6) often mesh with this differential mechanism gear ring (29) simultaneously.
9. seven speed dual clutch formula automatic transmission as claimed in claim 8, it is characterized in that: this inputs two axle driving gears (31), this centre idle pulley (15) and this input countershaft actuation gear (7) form the first co-planar gear set, this first final gear (30), this second final gear (6) and this differential mechanism gear ring (29) form the second co-planar gear set, this reverse driving gear (4), this reverse idler gear (37) and this reverse gear driven gear (5) form the 3rd co-planar gear set, wherein this first co-planar gear set is positioned at a wherein side of this second co-planar gear set, the 3rd co-planar gear set is positioned at the opposite side of this second co-planar gear set.
10. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this inputs two axles (35) is hollow shaft, this is inputted two axles (35) and is nested in this and inputs that an axle (18) is upper and to input an axle (18) coaxial with this.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420358500.8U CN203926635U (en) | 2014-06-30 | 2014-06-30 | Seven speed dual clutch formula automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420358500.8U CN203926635U (en) | 2014-06-30 | 2014-06-30 | Seven speed dual clutch formula automatic transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203926635U true CN203926635U (en) | 2014-11-05 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420358500.8U Expired - Fee Related CN203926635U (en) | 2014-06-30 | 2014-06-30 | Seven speed dual clutch formula automatic transmission |
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| Country | Link |
|---|---|
| CN (1) | CN203926635U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105202126A (en) * | 2014-06-30 | 2015-12-30 | 广州汽车集团股份有限公司 | Seven-speed double-clutch type automatic transmission |
| CN105697742A (en) * | 2016-03-11 | 2016-06-22 | 湖南中德汽车自动变速器股份有限公司 | Shift power compensation type power shift gearbox and shifting method |
-
2014
- 2014-06-30 CN CN201420358500.8U patent/CN203926635U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105202126A (en) * | 2014-06-30 | 2015-12-30 | 广州汽车集团股份有限公司 | Seven-speed double-clutch type automatic transmission |
| CN105697742A (en) * | 2016-03-11 | 2016-06-22 | 湖南中德汽车自动变速器股份有限公司 | Shift power compensation type power shift gearbox and shifting method |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| 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: 20141105 Termination date: 20210630 |