CN203926631U - Seven speed dual clutch formula automatic transmission - Google Patents
Seven speed dual clutch formula automatic transmission Download PDFInfo
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- CN203926631U CN203926631U CN201420358520.5U CN201420358520U CN203926631U CN 203926631 U CN203926631 U CN 203926631U CN 201420358520 U CN201420358520 U CN 201420358520U CN 203926631 U CN203926631 U CN 203926631U
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Abstract
A kind of seven speed dual clutch formula automatic transmission, comprise 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, the driving gear of odd number shelves is arranged on input one axle, the driving gear of even number shelves is arranged on input countershaft, the driven gear of odd number shelves is arranged on output one axle, the driven gear of even number shelves 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, then be delivered to again on part gear by input countershaft, 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, greatly shorten the axial length of whole speed changer, make the overall structure of speed changer more compact, 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, interrupt power at gearshift procedure, 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 ensure 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, particularly compact car, 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 make the more difficult optimum working zone that is operated in of motor, thereby power character and Economy to car load has 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, five grades of driving gears, third speed drive gear, seven grades of driving gears and one grade of driving gear are installed successively on this input one axle from one end, on these input two axles, are installed with input two axle driving gears;
First clutch, this first clutch is connected with this input one axle;
Second clutch, this second clutch is connected with these input two axles;
Export an axle, the first final gear, five grades of driven gears, third gear driven gear, seven grades of driven gears and first speed driven gear are installed successively on this output one axle from one end;
Export two axles, second gear driven gear, reverse gear driven gear, the second final gear, fourth gear driven gear and six grades of driven gears are installed successively on these output two axles from one end;
Input countershaft is provided with successively second gear driving gear, reverse driving gear, input countershaft actuation gear, fourth gear driving gear and six grades of driving gears 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 often engages with this first speed driven gear, this second gear driving gear often engages with this second gear driven gear, this third speed drive gear often engages with this third gear driven gear, this fourth gear driving gear often engages with this fourth gear driven gear, five grades of driven gears of these five grades of driving gears and this often engage, six grades of driven gears of these six grades of driving gears and this often engage, seven grades of driven gears of these seven grades of driving gears and this often engage, this reverse driving gear often engages with this reverse idler gear, this reverse idler gear often engages with this reverse gear driven gear, these input two axle driving gears often engage with this centre idle pulley, this centre idle pulley often engages with this input countershaft actuation gear,
One or seven grades of synchronizers, the joint of one grade of these or seven grades of synchronizer control and seven grades;
Two reversing-gear synchronizers, the joint of this two reversing-gear synchronizers control second gear and reverse gear;
Three Five-gear synchronizers, the joint of this three Five-gear synchronizers control third gear and five grades; And
Four or six grades of synchronizers, the joint of these four or six grades of synchronizer control fourth gear and six grades.
Further, this grade of driving gear and these seven grades of driving gears are fixed on this input one axle, this first speed driven gear and these seven grades of driven gear empty sets are on this output one axle, and these or seven grades of synchronizers are arranged on this output one axle and between this first speed driven gear and this seven grades of driven gears.
Further, this second gear driving gear and this reverse driving gear are fixed on this input countershaft, this second gear driven gear and this reverse gear driven gear empty set are on these output two axles, and this two reversing-gear synchronizer is arranged on these output two axles and between this second gear driven gear and this reverse gear driven gear.
Further, this third speed drive gear and these five grades of driving gears are fixed on this input one axle, this third gear driven gear and these five grades of driven gear empty sets are on this output one axle, and this three Five-gear synchronizer is arranged on this output one axle and between this third gear driven gear and this five grades of driven gears.
Further, this third speed drive gear and these five grades of driving gear empty sets are on this input one axle, this third gear driven gear and these five grades of driven gears are fixed on this output one axle, and this three Five-gear synchronizer is arranged on this input one axle and between these five grades of driving gears and this third speed drive gear.
Further, this fourth gear driving gear and these six grades of driving gear empty sets are on this input countershaft, this fourth gear driven gear and these six grades of driven gears are fixed on these output two axles, and these four or six grades of synchronizers are arranged on this input countershaft and between this fourth gear driving gear and this six grades of driving gears.
Further, this fourth gear driving gear and these six grades of driving gears are fixed on this input countershaft, this fourth gear driven gear and these six grades of driven gear empty sets are on these output two axles, and these four or six grades of synchronizers are arranged on these output two axles and between this fourth gear driven gear and this six grades of driven gears.
Further, this seven speed dual clutch formula automatic transmission also comprises differential mechanism gear ring, this first final gear is fixed on this output one axle, this second final gear is fixed on these output two axles, and this first final gear and this second final gear often engage with this differential mechanism gear ring simultaneously.
Further, these input two axle driving gears, this centre idle pulley and this input countershaft actuation gear are formed as the first co-planar gear set, this first final gear, this second final gear and this differential mechanism gear ring are formed as the second co-planar gear set, this reverse driving gear, this reverse idler gear and this reverse gear driven gear are formed as 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, these input two axles are hollow shaft, and these input two axles are nested on this input one axle and are coaxial with this input one axle.
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 be delivered to again on part gear (being second gear, fourth gear, six grades and reverse gear) by input countershaft, 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 shorten the axial length of whole speed changer, make the overall structure of speed changer more compact, arrangement is more reasonable.
(2) driving gear of each gear often engages with corresponding driven gear by the mode that adopts non-shared driving 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 with under the prerequisite of 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.
Brief description of the drawings
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, particularly a kind of seven speed dual clutch formula automatic transmission that is suitable for front transverse engine, forerunner's car, 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: second gear driving gear 1, second gear driven gear 2, two reversing-gear synchronizers 3, reverse driving gear 4, reverse gear driven gear 5, the second final gear 6, input countershaft actuation gear 7, fourth gear driven gear 8, fourth gear driving gear 9, four or six grades of synchronizers 10, six grades of driven gears 11, export two axles 12, six grades of driving gears 13, input countershaft 14, middle idle pulley 15, five grades of driving gears 16, third speed drive gear 17, input an axle 18, seven grades of driving gears 19, one grade of driving gear 20, one or seven grades of synchronizers 21, first speed driven gear 22, export an axle 23, seven grades of driven gears 24, third gear driven gear 25, three Five-gear synchronizers 26, five grades of driven gears 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 five grades of driving gears 16, third speed drive gear 17, seven grades of driving gears 19 and one grade of driving gear 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, five grades of driven gears 27, third gear driven gear 25, seven grades of driven gears 24 and first speed driven gears 22 are installed successively near motor one end.Export on two axles 12 from second gear driven gear 2, reverse gear driven gear 5, the second final gear 6, fourth gear driven gear 8 and six grades of driven gears 11 being installed successively near motor one end.On input countershaft 14, from second gear driving gear 1, reverse driving gear 4, input countershaft actuation gear 7, fourth gear driving gear 9 and six grades of driving gears 13 are installed successively near motor one end, this input countershaft actuation gear 7 is fixed on this 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 20 often engages with first speed driven gear 22; Second gear driving gear 1 often engages with second gear driven gear 2; Third speed drive gear 17 often engages with third gear driven gear 25; Fourth gear driving gear 9 often engages with fourth gear driven gear 8; Five grades of driving gears 16 often engage with five grades of driven gears 27; Six grades of driving gears 13 often engage with six grades of driven gears 11; Seven grades of driving gears 19 often engage with seven grades of driven gears 24; Reverse driving gear 4 often engages with reverse idler gear 37, reverse idler gear 37 often engages 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 engages with reverse driving gear 4 indirectly by reverse idler gear 37; Input two axle driving gears 31 and often engage with middle idle pulley 15, middle idle pulley 15 often engages with input countershaft actuation gear 7.
Input two axle driving gears 31, middle idle pulley 15 and input countershaft actuation gear 7 and be formed as 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 engage with differential mechanism gear ring 29 simultaneously, and the first final gear 30, the second final gear 6 and differential mechanism gear ring 29 are formed as the second co-planar gear set.Reverse driving gear 4, reverse idler gear 37 and reverse gear driven gear 5 are formed as 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 20 and seven grades of driving gears 19 are fixed on input one axle 18, first speed driven gear 22 and seven grades of driven gear 24 empty sets are on output one axle 23, one or seven grades of synchronizers 21 are arranged on output one axle 23 and between first speed driven gear 22 and seven grades of driven gears 24, are controlled and are engaged for one grade with seven grades by one or seven grades of synchronizers 21.
Second gear driving gear 1 and reverse driving gear 4 are fixed on input countershaft 14, second gear driven gear 2 and reverse gear driven gear 5 empty sets are on output two axles 12, two reversing-gear synchronizers 3 are arranged on output two axles 12 and between second gear driven gear 2 and reverse gear driven gear 5, second gear is controlled and engaged by two reversing-gear synchronizers 3 with reverse gear.
In the present embodiment, third speed drive gear 17 and five grades of driving gears 16 are fixed on input one axle 18, third gear driven gear 25 and five grades of driven gear 27 empty sets are on output one axle 23, three Five-gear synchronizers 26 are arranged on output one axle 23 and between third gear driven gear 25 and five grades of driven gears 27, third gear is controlled and engaged by three Five-gear synchronizers 26 with five grades.
In the present embodiment, fourth gear driving gear 9 and six grades of driving gear 13 empty sets are on input countershaft 14, fourth gear driven gear 8 and six grades of driven gears 11 are fixed on output two axles 12, four or six grades of synchronizers 10 are arranged on input countershaft 14 and between fourth gear driving gear 9 and six grades of driving gears 13, fourth gear is controlled and engaged by four or six grades of synchronizers 10 with six grades.
The automatic transmission of the present embodiment each grade of power transmission in the time of work is as follows:
One grade of power transmission route: one or seven grades of synchronizers 21 and first speed driven gear 22 engage, first clutch 33 closures, Engine torque passes to input one axle 18 by first clutch 33, pass to first speed driven gear 22 via one grade of driving gear 20, transfer torque to the first final gear 30 on output one axle 23 by first speed driven gear 22 and engaging of one or seven grades of synchronizers 21 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Second gear power transmission line: two reversing-gear synchronizers 3 and second gear driven gear 2 engage, second clutch 34 closures, Engine torque passes to input two axles 35 by second clutch 34, pass to input countershaft 14 and second gear driving gear 1 via input two axle driving gears 31, middle idle pulley 15, input countershaft actuation gear 7, transfer torque to the second final gear 6 on output two axles 12 by the joint of second gear driven gear 2 and two reversing-gear synchronizers 3 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Third gear power transmission route: three Five-gear synchronizers 26 and third gear driven gear 25 engage, first clutch 33 closures, Engine torque passes to input one axle 18 by first clutch 33, pass to third gear driven gear 25 via third speed drive gear 17, transfer torque to the first final gear 30 on output one axle 23 by third gear driven gear 25 and engaging of three Five-gear synchronizers 26 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Fourth gear power transmission line: four or six grades of synchronizers 10 and fourth gear driving gear 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, transferred torque on fourth gear driven gear 8 by the joint of 9 and 46 grades of synchronizers 10 of fourth gear driving gear again, be delivered to the second final gear 6 on output two axles 12 by fourth gear driven gear 8, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Five grades of power transmission routes: three Five-gear synchronizers 26 and five grades of driven gears 27 engage, first clutch 33 closures, Engine torque passes to input one axle 18 by first clutch 33, pass to five grades of driven gears 27 via five grades of driving gears 16, transfer torque to the first final gear 30 on output one axle 23 by five grades of driven gears 27 and engaging of three Five-gear synchronizers 26 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Six grades of power transmission lines: four or six grades of synchronizers 10 and six grades of driving gears 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, transferred torque on six grades of driven gears 11 by the joint of 13 and 46 grades of synchronizers 10 of six grades of driving gears again, be delivered to the second final gear 6 on output two axles 12 by six grades of driven gears 11, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Seven grades of power transmission routes: one or seven grades of synchronizers 21 and seven grades of driven gears 24 engage, first clutch 33 closures, Engine torque passes to input one axle 18 by first clutch 33, pass to seven grades of driven gears 24 via seven grades of driving gears 19, transfer torque to the first final gear 30 on output one axle 23 by seven grades of driven gears 24 and engaging of one or seven grades of synchronizers 21 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
Reverse gear power transmission line: two reversing-gear synchronizers 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, transfer torque to the second final gear 6 on output two axles 12 by two reversing-gear synchronizers 3 and engaging of reverse gear driven gear 5 again, again by differential mechanism gear ring 29, and finally by differential mechanism 28 outputting powers.
One grade is changed second gear process: one grade time, one or seven grades of synchronizers 21 and first speed driven gear 22 engage, first clutch 33 closures, and second clutch 34 is opened; Dual-clutch transmission control system is sent one grade and is changed after second gear instruction, gear shifting actuating mechanism engages two reversing-gear synchronizers 3 and second gear driven gear 2 in advance, now second clutch 34 is still in open mode, i.e. transferring power not of second clutch 34 and input two axles 35; Along with shift process continues, first clutch 33 is opened gradually, and meanwhile second clutch 34 is closed gradually, in this process, has all the time clutch to engage, and there will not be torque break; First clutch 33 is opened completely, after the complete closure of second clutch 34, shift process finishes.Gear is now second gear, and first clutch 33 is in open mode, i.e. first clutch 33, not transferring power of input one axle 18, and engine power is delivered on second gear driven gear 2 via second clutch 34.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 speed drive gear 17 and five grades of driving gear 16 empty sets are on input one axle 18, third gear driven gear 25 and five grades of driven gears 27 are fixed on output one axle 23, and three Five-gear synchronizers 26 are arranged on input one axle 18 and between third speed drive gear 17 and five grades of driving gears 16; Fourth gear driving gear 9 and six grades of driving gears 13 are fixed on input countershaft 14, fourth gear driven gear 8 and six grades of driven gear 11 empty sets are on output two axles 12, and four or six grades of synchronizers 10 are arranged on output two axles 12 and between fourth gear driven gear 8 and six grades of driven gears 11.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 17 and five grades of driving gears 16 are fixed on input one axle 18, third gear driven gear 25 and five grades of driven gear 27 empty sets are on output one axle 23, and three Five-gear synchronizers 26 are arranged on output one axle 23 and between third gear driven gear 25 and five grades of driven gears 27; Fourth gear driving gear 9 and six grades of driving gears 13 are fixed on input countershaft 14, fourth gear driven gear 8 and six grades of driven gear 11 empty sets are on output two axles 12, and four or six grades of synchronizers 10 are arranged on output two axles 12 and between fourth gear driven gear 8 and six grades of driven gears 11.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 speed drive gear 17 and five grades of driving gear 16 empty sets are on input one axle 18, third gear driven gear 25 and five grades of driven gears 27 are fixed on output one axle 23, and three Five-gear synchronizers 26 are arranged on input one axle 18 and between third speed drive gear 17 and five grades of driving gears 16; Fourth gear driving gear 9 and six grades of driving gear 13 empty sets are on input countershaft 14, fourth gear driven gear 8 and six grades of driven gears 11 are fixed on output two axles 12, and four or six grades of synchronizers 10 are arranged on input countershaft 14 and between fourth gear driving gear 9 and six grades of driving gears 13.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, a middle idle pulley supporting axle, a reverse gear shaft, this automatic transmission has seven forward gears and a reverse gear, the driving gear of odd number shelves is arranged on input one axle, the driving gear of even number shelves is arranged on input countershaft, the driven gear of odd number shelves is arranged on output one axle, the driven gear of even number shelves is arranged on output two axles, and 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 be delivered to again on part gear (being second gear, fourth gear, six grades and reverse gear) by input countershaft, 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 shorten the axial length of whole speed changer, make the overall structure of speed changer more compact, arrangement is more reasonable.
(2) driving gear of each gear often engages with corresponding driven gear by the mode that adopts non-shared driving 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 with under the prerequisite of 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.Should be appreciated that the use of the described noun of locality should not limit the scope of the application's request 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 amendment 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 input one axle (18) is upper is provided with successively five grades of driving gears (16), third speed drive gear (17), seven grades of driving gears (19) and one grade of driving gear (20) from one end, is installed with input two axle driving gears (31) on these input two axles (35);
First clutch (33), this first clutch (33) is connected with this input one axle (18);
Second clutch (34), this second clutch (34) is connected with these input two axles (35);
Export an axle (23), upper the first final gear (30), five grades of driven gears (27), third gear driven gear (25), seven grades of driven gears (24) and the first speed driven gear (22) of being provided with successively of this output one axle (23) from one end;
Export two axles (12), upper second gear driven gear (2), reverse gear driven gear (5), the second final gear (6), fourth gear driven gear (8) and the six grades of driven gears (11) of being provided with successively of these output two axles (12) from one end;
Input countershaft (14), upper second gear driving gear (1), reverse driving gear (4), input countershaft actuation gear (7), fourth gear driving gear (9) and the six grades of driving gears (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 (20) often engages with this first speed driven gear (22), this second gear driving gear (1) often engages with this second gear driven gear (2), this third speed drive gear (17) often engages with this third gear driven gear (25), this fourth gear driving gear (9) often engages with this fourth gear driven gear (8), these five grades of driving gears (16) often engage with these five grades of driven gears (27), these six grades of driving gears (13) often engage with these six grades of driven gears (11), these seven grades of driving gears (19) often engage with these seven grades of driven gears (24), this reverse driving gear (4) often engages with this reverse idler gear (37), this reverse idler gear (37) often engages with this reverse gear driven gear (5), these input two axle driving gears (31) often engage with this centre idle pulley (15), this centre idle pulley (15) often engages with this input countershaft actuation gear (7),
One or seven grades of synchronizers (21), this one or seven grades of synchronizers (21) are controlled the joint of a grade and seven grades;
Two reversing-gear synchronizers (3), this two reversing-gear synchronizer (3) is controlled the joint of second gear and reverse gear;
Three Five-gear synchronizers (26), this three Five-gear synchronizer (26) is controlled the joint of third gear and five grades; And
Four or six grades of synchronizers (10), this four or six grades of synchronizers (10) are controlled the joint of fourth gear and six 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 (20) and this seven grades of driving gears (19) are fixed on this input one axle (18), this first speed driven gear (22) and this seven grades of driven gears (24) empty set are upper at this output one axle (23), and these one or seven grades of synchronizers (21) are arranged on this output one axle (23) above and are positioned between this first speed driven gear (22) and this seven grades of driven gears (24).
3. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this second gear driving gear (1) and this reverse driving gear (4) are fixed on this input countershaft (14), this second gear driven gear (2) and this reverse gear driven gear (5) empty set are upper at these output two axles (12), and this two reversing-gear synchronizer (3) is arranged on these output two axles (12) above and is positioned between this second gear driven gear (2) and this reverse gear driven gear (5).
4. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this third speed drive gear (17) and this five grades of driving gears (16) are fixed on this input one axle (18), this third gear driven gear (25) and this five grades of driven gears (27) empty set are upper at this output one axle (23), and this three Five-gear synchronizer (26) is arranged on this output one axle (23) above and is positioned between this third gear driven gear (25) and this five grades of driven gears (27).
5. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this third speed drive gear (17) and this five grades of driving gears (16) empty set are on this input one axle (18), it is upper that this third gear driven gear (25) and this five grades of driven gears (27) are fixed on this output one axle (23), and this three Five-gear synchronizer (26) is arranged on this input one axle (18) above and is positioned between these five grades of driving gears (16) and this third speed drive gear (17).
6. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this fourth gear driving gear (9) and this six grades of driving gears (13) empty set are on this input countershaft (14), it is upper that this fourth gear driven gear (8) and this six grades of driven gears (11) are fixed on these output two axles (12), and these four or six grades of synchronizers (10) are arranged on this input countershaft (14) above and are positioned between this fourth gear driving gear (9) and this six grades of driving gears (13).
7. seven speed dual clutch formula automatic transmission as claimed in claim 1, it is characterized in that: this fourth gear driving gear (9) and this six grades of driving gears (13) are fixed on this input countershaft (14), this fourth gear driven gear (8) and this six grades of driven gears (11) empty set are upper at these output two axles (12), and these four or six grades of synchronizers (10) are arranged on these output two axles (12) above and are positioned between this fourth gear driven gear (8) and this six grades of driven gears (11).
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 output one axle (23), it is upper that this second final gear (6) is fixed on these output two axles (12), and this first final gear (30) and this second final gear (6) often engage 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: these input two axle driving gears (31), this centre idle pulley (15) and this input countershaft actuation gear (7) are formed as the first co-planar gear set, this first final gear (30), this second final gear (6) and this differential mechanism gear ring (29) are formed as the second co-planar gear set, this reverse driving gear (4), this reverse idler gear (37) and this reverse gear driven gear (5) are formed as 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: these input two axles (35) are hollow shaft, it is upper and coaxial with this input one axle (18) that these input two axles (35) are nested in this input one axle (18).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420358520.5U CN203926631U (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 |
|---|---|---|---|
| CN201420358520.5U CN203926631U (en) | 2014-06-30 | 2014-06-30 | Seven speed dual clutch formula automatic transmission |
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| Publication Number | Publication Date |
|---|---|
| CN203926631U true CN203926631U (en) | 2014-11-05 |
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|---|---|---|---|
| CN201420358520.5U Expired - Fee Related CN203926631U (en) | 2014-06-30 | 2014-06-30 | Seven speed dual clutch formula automatic transmission |
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| Country | Link |
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| CN (1) | CN203926631U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443673A (en) * | 2014-06-30 | 2016-03-30 | 广州汽车集团股份有限公司 | Seven-speed dual-clutch type automatic gearbox |
| 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 CN201420358520.5U patent/CN203926631U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443673A (en) * | 2014-06-30 | 2016-03-30 | 广州汽车集团股份有限公司 | Seven-speed dual-clutch type automatic gearbox |
| 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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