CN105443673A - Seven-speed dual-clutch type automatic gearbox - Google Patents
Seven-speed dual-clutch type automatic gearbox Download PDFInfo
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- CN105443673A CN105443673A CN201410310308.6A CN201410310308A CN105443673A CN 105443673 A CN105443673 A CN 105443673A CN 201410310308 A CN201410310308 A CN 201410310308A CN 105443673 A CN105443673 A CN 105443673A
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Abstract
A seven-speed dual-clutch type automatic gearbox comprises two embedded input shafts, two output shafts, an input countershaft, a middle idler wheel bearing shaft, and a reverse gear shaft; the automatic gearbox has 7 forward gears and a reverse gear; driving gear wheels of odd gears are arranged on the input shaft 1; driving gear wheels of even gears are arranged on the input countershaft; driven gear wheels of odd gears are arranged on the output shaft 1; driven gear wheels of even gears are arranged on the output shaft 2; the middle idler wheel bearing shaft is sleeved by a middle idler wheel in a hollow manner; the middle idler wheel can transfer the engine power from the input shaft 2 to the input countershaft, and can transfer the power from the input countershaft to certain gear position; the driving gear wheel of the gear position is arranged on the input countershaft, so the driving gear wheels of all gear positions need not to be arranged on the two input shafts in sequence, thus greatly reducing axial length of the whole gearbox; the gearbox is more compact in whole structure, and whole vehicle can be arranged more reasonable.
Description
Technical field
The present invention relates to the transmission technology field of automobile, particularly relate to a kind of seven speed dual clutch formula automatic transmission.
Background technique
Double-clutch automatic transmission is integrated in a gearbox by two gearboxes and two clutches, two input shafts connected together rotationally are connected with one of them clutch respectively, two input shafts transmit the power of two gearbox speed groups respectively, by automatically switching between two clutches thus completing gearshift program, therefore the power shfit of gearshift procedure can be realized, namely power is interrupted 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 that the acceleration of vehicle, and no longer produce the abrupt deceleration situation because gear shift causes due to vehicle, also the travelling comfort of vehicle operating is improved greatly.
In existing double-clutch automatic transmission, the driving gear of all gears is arranged on the first input shaft and the second input shaft successively, therefore the axial dimension of speed changer is longer, so for the such vehicle of front transverse engine, front-wheel drive, particularly compact car, because installing space is restricted, above-mentioned speed changer is more difficult employing just.Secondly, when partial gear adopts shared driving gear, although relatively can reduce the axial dimension of speed changer, gear-driven speed ratio error may be comparatively large, and speed ratio needed for more difficult realization, is unfavorable for making motor in best region work.In addition, existing speed changer due to the gear of speed change less, mostly generally be most six grades, the more difficult reasonable distribution realizing velocity ratio, make that motor is more difficult is operated in optimum working zone, thus the power character of car load and Economy are had a negative impact.
Summary of the invention
In view of this, be necessary to provide a kind of seven speed dual clutch formula automatic transmission, it can shorten the axial length of speed changer, enables actual speed ratio more close to required speed ratio, velocity ratio is distributed more reasonable.
Embodiments of the invention provide a kind of seven speed dual clutch formula automatic transmission, comprising:
Input one axle and input two axles of mutually nested setting, this input one axle is provided with from one end five grades of driving gears, third speed drive gear, seven grades of driving gears and one grade of driving gear successively, this input two axle is installed with input two axle driving gear;
First clutch, this first clutch is connected with this input one axle;
Second clutch, this second clutch is connected with this input two axle;
Export an axle, this output one axle is provided with from one end the first final gear, five grades of driven gears, third gear driven gear, seven grades of driven gears and first speed driven gears successively;
Export two axles, this output two axle is provided with from one end second gear driven gear, reverse gear driven gear, the second final gear, fourth gear driven gear and six grades of driven gears successively;
Input countershaft, this input countershaft is provided with from one end second gear driving gear, reverse driving gear, input countershaft actuation gear, fourth gear driving gear and six grades of driving gears successively, this input countershaft actuation gear is fixed on this input countershaft;
Intermediate idler supporting axle, on this intermediate idler supporting axle, empty set is provided with intermediate idler;
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, these five grades of driving gears and this five grades of driven gears often engage, these six grades of driving gears and this six grades of driven gears often engage, these seven grades of driving gears and this seven grades of driven gears 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, this input two axle driving gear often engages with this intermediate idler, this intermediate idler often engages with this input countershaft actuation gear,
One or seven grades of synchronizers, these or seven grades of synchronizers control the joint of a grade and seven grades;
Two reversing-gear synchronizers, this two reversing-gear synchronizer controls the joint of second gear and reverse gear;
Three Five-gear synchronizers, this three Five-gear synchronizer controls the joint of third gear and five grades; And
Four or six grades of synchronizers, these four or six grades of synchronizers control the joint of 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 to be 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 this output two axle, and this two reversing-gear synchronizer to be arranged on this output two axle 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 to be 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 to be 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 this output two axle, and these four or six grades of synchronizers to be 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 this output two axle, and these four or six grades of synchronizers to be arranged on this output two axle 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 this output two axle, and this first final gear and this second final gear often engage with this differential mechanism gear ring simultaneously.
Further, this input two axle driving gear, this intermediate idler 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 the 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 input two axle is hollow shaft, and this input two axle to be nested on this input one axle and coaxial with this input one axle.
The beneficial effect that the technological scheme that embodiments of the invention provide is brought is:
(1) by an intermediate idler, engine power is delivered to input countershaft from input two axle, then be delivered on partial gear (i.e. second gear, fourth gear, six grades and reverse gear) again by input countershaft, the driving gear of this partial gear is arranged on input countershaft, thus the driving gear of all gears is without the need to being arranged on input one axle and input two axles successively, substantially reduce 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 adopting the mode of non-common driving gear, namely 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 of shared driving gear, make actual speed ratio more close to required speed ratio, power character and the Economy of car load can be improved;
(3) because entire length size obviously shortens, therefore seven forward gearss can be set with under the prerequisite of common five, identical external dimension of six-speed gearbox, thus making gear range become large, velocity ratio distributes more reasonable, and then significantly improves power performance and the car load class of car load.
Accompanying drawing explanation
Fig. 1 is the structural representation of the seven speed dual clutch formula automatic transmission of first embodiment of the invention.
Fig. 2 is the structural representation of the seven speed dual clutch formula automatic transmission of second embodiment of the invention.
Embodiment
The invention provides a kind of seven speed dual clutch formula automatic transmission, particularly a kind of seven speed dual clutch formula automatic transmission being suitable for front transverse engine, forerunner's car, the problems such as the 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 object, technical solutions and advantages of the present invention clearly, below in conjunction with accompanying drawing, embodiment of the present invention is further described.
First embodiment
Fig. 1 is the structural representation of the seven speed dual clutch formula automatic transmission of first embodiment of the invention, 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, 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, intermediate idler 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, first final gear 30, input two axle driving gears 31, engine crankshaft 32, first clutch 33, second clutch 34, input two axles 35, intermediate idler supporting axle 36, reverse idler gear 37, and reverse gear shaft 38.
This automatic transmission comprises seven axles, is respectively: input an axle 18, input two axles 35, export an axle 23, export two axles 12, input countershaft 14, intermediate idler supporting axle 36 and reverse gear shaft 38, seven axles are parallel to each other layout.Input on an axle 18, near motor one end, 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.Input on two axles 35 and be installed with input two axle driving gear 31.Export on an axle 23, near motor one end, 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 gear 22 are installed successively.Export on two axles 12, near motor one end, second gear driven gear 2, reverse gear driven gear 5, second final gear 6, fourth gear driven gear 8 and six grades of driven gears 11 are installed successively.From being provided with 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 near motor one end successively on input countershaft 14, this input countershaft actuation gear 7 is fixed on this input countershaft 14.On intermediate idler supporting axle 36, empty set is provided with intermediate idler 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, inputting two axles 35 is hollow shaft, inputs two axles 35 and to be nested on input one axle 18 and coaxial with input one axle 18.First clutch 33 is connected with input one axle 18 and for control inputs one axle 18, and second clutch 34 is connected with input two axle 35 and for control inputs two axle 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, namely do not have direct meshing relation between reverse driving gear 4 and reverse gear driven gear 5, reverse gear driven gear 5 is engaged with reverse driving gear 4 indirectly by reverse idler gear 37; Input two axle driving gears 31 often to engage with intermediate idler 15, intermediate idler 15 often engages with input countershaft actuation gear 7.
Input two axle driving gears 31, intermediate idler 15 and input countershaft actuation gear 7 and be formed as the first co-planar gear set.First final gear 30 is fixed on output one axle 23.Second final gear 6 is fixed on output two axle 12, 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, 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, one grade is controlled to engage by one or seven grades of synchronizers 21 with seven grades.
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 set are on output two axle 12, two reversing-gear synchronizers 3 are arranged on output two axle 12 and between second gear driven gear 2 and reverse gear driven gear 5, second gear is controlled to engage 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 to engage 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 axle 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 to engage by four or six grades of synchronizers 10 with six grades.
Operationally each shelves power transmission is as follows for the automatic transmission of the present embodiment:
One grade of power transmission route: one or seven grades of synchronizers 21 and first speed driven gear 22 engage, first clutch 33 closes, Engine torque passes to input one axle 18 by first clutch 33, first speed driven gear 22 is passed to via one grade of driving gear 20, the first final gear 30 on output one axle 23 is transferred torque to again by the joint of first speed driven gear 22 and one or seven grades of synchronizers 21, again by differential mechanism gear ring 29, and final by differential mechanism 28 outputting power.
Second gear power transmission line: two reversing-gear synchronizers 3 and second gear driven gear 2 engage, second clutch 34 closes, Engine torque passes to input two axle 35 by second clutch 34, input countershaft 14 and second gear driving gear 1 is passed to via input two axle driving gear 31, intermediate idler 15, input countershaft actuation gear 7, the second final gear 6 on output two axle 12 is transferred torque to again by the joint of second gear driven gear 2 and two reversing-gear synchronizers 3, again by differential mechanism gear ring 29, and final by differential mechanism 28 outputting power.
Third gear power transmission route: three Five-gear synchronizers 26 and third gear driven gear 25 engage, first clutch 33 closes, Engine torque passes to input one axle 18 by first clutch 33, third gear driven gear 25 is passed to via third speed drive gear 17, the first final gear 30 on output one axle 23 is transferred torque to again by the joint of third gear driven gear 25 and three Five-gear synchronizers 26, again by differential mechanism gear ring 29, and final by differential mechanism 28 outputting power.
Fourth gear power transmission line: four or six grades of synchronizers 10 and fourth gear driving gear 9 engage, second clutch 34 closes, Engine torque passes to input two axle 35 by second clutch 34, via input two axle driving gear 31, intermediate idler 15, input countershaft actuation gear 7 passes on input countershaft 14, transfer torque on fourth gear driven gear 8 by the joint of fourth gear driving gear 9 and four or six grades of synchronizers 10 again, the second final gear 6 on output two axle 12 is delivered to by fourth gear driven gear 8, again by differential mechanism gear ring 29, and it is final by differential mechanism 28 outputting power.
Five grades of power transmission routes: three Five-gear synchronizers 26 and five grades of driven gears 27 engage, first clutch 33 closes, Engine torque passes to input one axle 18 by first clutch 33, five grades of driven gears 27 are passed to via five grades of driving gears 16, the first final gear 30 on output one axle 23 is transferred torque to again by the joint of five grades of driven gears 27 and three Five-gear synchronizers 26, again by differential mechanism gear ring 29, and final by differential mechanism 28 outputting power.
Six grades of power transmission lines: four or six grades of synchronizers 10 and six grades of driving gears 13 engage, second clutch 34 closes, Engine torque passes to input two axle 35 by second clutch 34, via input two axle driving gear 31, intermediate idler 15, input countershaft actuation gear 7 passes on input countershaft 14, transfer torque on six grades of driven gears 11 by the joint of six grades of driving gears 13 and four or six grades of synchronizers 10 again, the second final gear 6 on output two axle 12 is delivered to by six grades of driven gears 11, again by differential mechanism gear ring 29, and it is final by differential mechanism 28 outputting power.
Seven grades of power transmission routes: one or seven grades of synchronizers 21 and seven grades of driven gears 24 engage, first clutch 33 closes, Engine torque passes to input one axle 18 by first clutch 33, seven grades of driven gears 24 are passed to via seven grades of driving gears 19, the first final gear 30 on output one axle 23 is transferred torque to again by the joint of seven grades of driven gears 24 and one or seven grades of synchronizers 21, again by differential mechanism gear ring 29, and final by differential mechanism 28 outputting power.
Reverse gear power transmission line: two reversing-gear synchronizers 3 and reverse gear driven gear 5 engage, second clutch 34 closes, Engine torque passes to input two axle 35 by second clutch 34, via input two axle driving gear 31, intermediate idler 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, to be transferred torque to the second final gear 6 on output two axle 12 again with the joint of reverse gear driven gear 5 by two reversing-gear synchronizers 3, again by differential mechanism gear ring 29, and it is final by differential mechanism 28 outputting power.
One grade is changed second gear process: when one grade, and one or seven grades of synchronizers 21 and first speed driven gear 22 engage, and first clutch 33 closes, and second clutch 34 is opened; Dual-clutch transmission control system send one grade change second gear instruction after, two reversing-gear synchronizers 3 and second gear driven gear 2 engage by gear shifting actuating mechanism in advance, now second clutch 34 is still in open mode, i.e. second clutch 34 and input two axles 35 not transferring power; Along with shift process continues, first clutch 33 is opened gradually, and meanwhile second clutch 34 closes gradually, in this process, has clutch to engage all the time, there will not be torque break; First clutch 33 is opened completely, second clutch 34 completely closed after, shift process terminates.Gear is now second gear, and first clutch 33 is in open mode, namely first clutch 33, input an axle 18 not transferring power, 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, and the shift process between all the other gears that can draw the present embodiment, does not repeat them here for shift process between all the other gears of the present embodiment.
Second embodiment
Fig. 2 is the structural representation of the seven speed dual clutch formula automatic transmission of second embodiment of the invention, please refer to the drawing 2, the difference of the automatic transmission of the present embodiment and the automatic transmission of the first embodiment 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 to be 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 axle 12, and four or six grades of synchronizers 10 to be arranged on output two axle 12 and between fourth gear driven gear 8 and six grades of driven gears 11.With reference to above-mentioned first embodiment, can not repeat them here about other structures of the present embodiment and working principle.
It is also understood that ground, in the third embodiment of the present invention, 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 to be 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 axle 12, and four or six grades of synchronizers 10 to be arranged on output two axle 12 and between fourth gear driven gear 8 and six grades of driven gears 11.With reference to above-mentioned first embodiment, can not repeat them here about other structures of the present embodiment and working principle.
It is also understood that ground, in the fourth embodiment of the present invention, 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 to be 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 axle 12, and four or six grades of synchronizers 10 to be arranged on input countershaft 14 and between fourth gear driving gear 9 and six grades of driving gears 13.With reference to above-mentioned first embodiment, can not repeat them here about other structures of the present embodiment and working principle.
The double-clutch automatic transmission of the embodiment of the present invention comprises two coaxially arranged input shafts, two output shafts, an input countershaft, intermediate idler 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 axle, and on intermediate idler supporting axle, empty set is provided with intermediate idler.The seven speed dual clutch formula automatic transmission of the present embodiment has following beneficial effect:
(1) by an intermediate idler, engine power is delivered to input countershaft from input two axle, then be delivered on partial gear (i.e. second gear, fourth gear, six grades and reverse gear) again by input countershaft, the driving gear of this partial gear is arranged on input countershaft, thus the driving gear of all gears is without the need to being arranged on input one axle and input two axles successively, substantially reduce 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 adopting the mode of non-common driving gear, namely 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 of shared driving gear, make actual speed ratio more close to required speed ratio, power character and the Economy of car load can be improved;
(3) because entire length size obviously shortens, therefore seven forward gearss can be set with under the prerequisite of common five, identical external dimension of six-speed gearbox, thus making gear range become large, velocity ratio distributes more reasonable, and then significantly improves 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 clearly do not listed.
In this article, the involved noun of locality such as forward and backward, upper and lower is arranged in figure with component in accompanying drawing and component position each other defines, clear and convenient just in order to 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.
When not conflicting, the feature in embodiment herein-above set forth and embodiment can be combined with each other.
The foregoing is only preferred embodiment of the present invention, not in order to limit the present invention, within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. a seven speed dual clutch formula automatic transmission, is characterized in that, comprising:
Input one axle (18) and the input two axles (35) of mutually nested setting, this input one axle (18) is provided with from one end five grades of driving gears (16), third speed drive gear (17), seven grades of driving gears (19) and one grade of driving gear (20) successively, this input two axle (35) is installed with input two axle driving gear (31);
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 this input two axle (35);
Export an axle (23), this output one axle (23) is provided with from one end 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) successively;
Export two axles (12), this output two axle (12) is provided with from one end 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) successively;
Input countershaft (14), this input countershaft (14) is provided with from one end 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) successively, this input countershaft actuation gear (7) is fixed on this input countershaft (14);
Intermediate idler supporting axle (36), the upper empty set of this intermediate idler supporting axle (36) is provided with intermediate idler (15);
Reverse gear shaft (38), the upper empty set of this reverse gear shaft (38) is provided with reverse idler gear (37), wherein, this grade of driving gear (20) is often engaged 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) and this five grades of driven gears (27) are often engaged, these six grades of driving gears (13) and this six grades of driven gears (11) are often engaged, these seven grades of driving gears (19) and this seven grades of driven gears (24) are often engaged, 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), this input two axle driving gear (31) often engages with this intermediate idler (15), this intermediate idler (15) often engages with this input countershaft actuation gear (7),
One or seven grades of synchronizers (21), these or seven grades of synchronizers (21) control the joint of a grade and seven grades;
Two reversing-gear synchronizers (3), this two reversing-gear synchronizer (3) controls the joint of second gear and reverse gear;
Three Five-gear synchronizers (26), this three Five-gear synchronizer (26) controls the joint of third gear and five grades; And
Four or six grades of synchronizers (10), these four or six grades of synchronizers (10) control 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 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 gear (24) empty sets are on this output one axle (23), and these or seven grades of synchronizers (21) are arranged on this output one axle (23) and go up and be 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 on this output two axle (12), and this two reversing-gear synchronizer (3) is arranged on this output two axle (12) and goes up and be 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 gear (27) empty sets are on this output one axle (23), and this three Five-gear synchronizer (26) is arranged on this output one axle (23) and goes up and be 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 gear (16) empty sets are on this input one axle (18), 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) and goes up and be 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 gear (13) empty sets are on this input countershaft (14), this fourth gear driven gear (8) and this six grades of driven gears (11) are fixed on this output two axle (12), and these four or six grades of synchronizers (10) are arranged on this input countershaft (14) and go up and be 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 gear (11) empty sets are on this output two axle (12), and these four or six grades of synchronizers (10) are arranged on this output two axle (12) and go up and be 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), this second final gear (6) is fixed on this output two axle (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: this input two axle driving gear (31), this intermediate idler (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 the wherein side of this second co-planar gear set, 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 input two axle (35) is hollow shaft, it is upper and coaxial with this input one axle (18) that this input two axle (35) is nested in this input one axle (18).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410310308.6A CN105443673A (en) | 2014-06-30 | 2014-06-30 | Seven-speed dual-clutch type automatic gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410310308.6A CN105443673A (en) | 2014-06-30 | 2014-06-30 | Seven-speed dual-clutch type automatic gearbox |
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| Publication Number | Publication Date |
|---|---|
| CN105443673A true CN105443673A (en) | 2016-03-30 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410310308.6A Pending CN105443673A (en) | 2014-06-30 | 2014-06-30 | Seven-speed dual-clutch type automatic gearbox |
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| CN (1) | CN105443673A (en) |
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| CN203926631U (en) * | 2014-06-30 | 2014-11-05 | 广州汽车集团股份有限公司 | Seven speed dual clutch formula automatic transmission |
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| CN101057091A (en) * | 2004-09-24 | 2007-10-17 | 大众汽车有限公司 | Sensor system and method for controlling an automated dual clutch transmission |
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Application publication date: 20160330 |