CN105443678A - Ten-speed dual clutch automatic transmission - Google Patents
Ten-speed dual clutch automatic transmission Download PDFInfo
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- CN105443678A CN105443678A CN201410436278.3A CN201410436278A CN105443678A CN 105443678 A CN105443678 A CN 105443678A CN 201410436278 A CN201410436278 A CN 201410436278A CN 105443678 A CN105443678 A CN 105443678A
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Abstract
The invention discloses a ten-speed dual clutch automatic transmission. The ten-speed dual clutch automatic transmission comprises an internal input shaft, an external input shaft, a first internal output shaft, a first external output shaft, a second internal output shaft and a second external output shaft, wherein the internal input shaft is nested in the external input shaft, the first internal output shaft is nested in the first external output shaft, and the second internal output shaft is nested in the second external output shaft. According to the automatic transmission, the two sets of output shaft structures arranged in a nest mode are adopted, and power transmission between the two output shafts arranged in the nest mode in each set is achieved through a synchronizer; ten forward gears and one reverse gear are achieved in a gear sharing way; a whole gearbox is compact in structure and small in axial size, the required installation space is small, the structure is simple, and machining is easy; the ten gears can be set on the premise that the external dimension of the ten-speed dual clutch automatic transmission is the same as that of an ordinary transmission with seven or eight gears, and the transmission ratio distribution is more reasonable, so that the probability that an engine works in the optimal area is higher, and the power performance and economical efficiency are improved.
Description
Technical field
The present invention relates to the transmission technology field of vehicle, particularly relate to a kind of ten fast double-clutch automatic gearboxes.
Background technique
Double-clutch automatic gearbox (DualClutchTransmission, DCT) be that two gearboxes and two clutches are integrated in a gearbox, 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 electric-controlled mechanical automatic speed transmission (AutomatedMechanicalTransmission, AMT) shortcoming of 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.
But, existing double-clutch automatic gearbox mostly is and adopts double output shaft or single output shaft, therefore its axial dimension is longer, so for the such vehicle, particularly compact car of front transverse engine, front-wheel drive, because its installing space is restricted, above-mentioned speed changer is more difficult employing just, and due to the gear of its speed change less, 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 ten fast double-clutch automatic gearboxes, its compact structure axial dimension is little, owing to having ten advance gears, velocity ratio is distributed more reasonable.
Embodiments of the invention provide a kind of ten fast double-clutch automatic gearboxes, comprising:
The interior input shaft of mutually nested setting and outer input shaft, interior input shaft is provided with ten grades of driving gears, six grades of driving gears, fourth gear driving gear and second gear driving gears successively near motor one end, outer input shaft is provided with seven grades of driving gears, nine grades of driving gears and third speed drive gear successively near motor one end;
The first clutch be connected with interior input shaft;
The second clutch be connected with outer input shaft;
Mutually nested setting first in output shaft and the first outer output shaft, in first on output shaft and the first outer output shaft from being provided with the first final gear, nine grades of driven gears, the 6th synchronizer, third gear driven gear, ten grades of driven gears, the 5th synchronizer, fourth gear driven gear and the 4th synchronizers near motor one end successively; Wherein, the first final gear, nine grades of driven gears and the 4th synchronizer are arranged in first on output shaft, and the 6th synchronizer, third gear driven gear, ten grades of driven gears, the 5th synchronizer and fourth gear driven gears are arranged on the first outer output shaft;
Mutually nested setting second in output shaft and the second outer output shaft, in second on output shaft and the second outer output shaft from being provided with the second final gear, seven grades of driven gears, the first synchronizer, reverse driving gear, the second synchronizer, six grades of driven gears, the 3rd synchronizer and second gear driven gears near motor one end successively; Wherein, the second final gear, seven grades of driven gears and the first synchronizer are arranged in second on output shaft, and reverse driving gear, the second synchronizer, six grades of driven gears, the 3rd synchronizer and second gear driven gears are arranged on the second outer output shaft;
Wherein, second gear driving gear often engages with second gear driven gear, third speed drive gear often engages with third gear driven gear, fourth gear driving gear often engages with fourth gear driven gear, six grades of driving gears often engage with six grades of driven gears, and seven grades of driving gears often engage with seven grades of driven gears, and nine grades of driving gears often engage with nine grades of driven gears, ten grades of driving gears often engage with ten grades of driven gears, and reverse driving gear often engages with third gear driven gear; Each gear on interior input shaft and outer input shaft is all fixed on corresponding axle or is directly formed on the axle of correspondence, in first in output shaft, the first outer output shaft, second on output shaft and the second outer output shaft except each gear equal empty set of the first final gear except the second final gear is on corresponding axle, first final gear to be fixed in first on output shaft, second final gear is fixed in second on output shaft, and the tooth hub of each synchronizer is all connected on corresponding axle.
Further, first synchronizer can engage with seven grades of driven gears and the second outer output shaft, second synchronizer can engage with reverse driving gear and six grades of driven gears, 3rd synchronizer can engage with second gear driven gear, 4th synchronizer can engage with the first outer output shaft, 5th synchronizer can engage with fourth gear driven gear and ten grades of driven gears, and the 6th synchronizer can engage with nine grades of driven gears and third gear driven gear.
Further, first synchronizer can engage with seven grades of driven gears and the second outer output shaft, second synchronizer can engage with reverse driving gear, 3rd synchronizer can engage with six grades of driven gears and second gear driven gear, 4th synchronizer can engage with the first outer output shaft, 5th synchronizer can engage with fourth gear driven gear and ten grades of driven gears, and the 6th synchronizer can engage with nine grades of driven gears and third gear driven gear.
Further, the first outer output shaft is provided with the first joining portion in the one end away from motor, and the 4th synchronizer can engage with the first joining portion.
Further, the second outer output shaft is provided with the second joining portion in the one end being close to motor, and the first synchronizer can engage with the second joining portion.
Further, this automatic transmission also comprises differential mechanism gear ring, and the first final gear and the second final gear often engage with differential mechanism gear ring simultaneously.
The ten fast double-clutch automatic gearboxes of the present embodiment, by adopting the output shaft structure of two groups of nested arrangement, realized the transmission of power by a synchronizer between two output shafts wherein often organizing nested arrangement, by using the mode of gear, achieve ten forward gears and a reverse gear, the compact axial dimension of whole gearbox designs is little, required installing space is less, structure is more simply easy to processing, with common seven, eight speed transmission can arrange ten gears under having the prerequisite of identical external dimension, it is more reasonable that velocity ratio distributes, motor is made to have more probability to be operated in its best region, improve power character and Economy.
Accompanying drawing explanation
Fig. 1 is the structural representation of ten fast double-clutch automatic gearboxes of the embodiment of the present invention.
Embodiment
The invention provides a kind of ten fast double-clutch automatic gearboxes, particularly a kind of ten fast double-clutch automatic gearboxes being applicable to front transverse engine, forerunner's car, the problems such as large, the required installing space of the axial length for existing double-clutch automatic gearbox is comparatively large, velocity ratio not easily distributes, gear number is few, provide the ten fast double-clutch automatic gearboxes that little, the required installing space of a kind of axial length is less, velocity ratio distributes comparatively rationally, gear number is more.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.
Fig. 1 is the structural representation of ten fast double-clutch automatic gearboxes of the embodiment of the present invention, please refer to the drawing 1, the automatic transmission of the present embodiment comprises: output shaft 1 in second, second final gear 2, seven grades of driven gears 3, first synchronizer 4, reverse driving gear 5, second synchronizer 6, six grades of driven gears 7, 3rd synchronizer 8, second gear driven gear 9, second outer output shaft 10, ten grades of driving gears 11, six grades of driving gears 12, second gear driving gear 13, interior input shaft 14, fourth gear driving gear 15, 4th synchronizer 16, output shaft 17 in first, first outer output shaft 18, fourth gear driven gear 19, 5th synchronizer 20, ten grades of driven gears 21, third gear driven gear 22, differential mechanism 23, differential mechanism gear ring 24, 6th synchronizer 25, first final gear 26, nine grades of driven gears 27, outer input shaft 28, motor 29, first clutch 30, second clutch 31, nine grades of driving gears 32, third speed drive gear 33 and seven grades of driving gears 34.
This automatic transmission comprises six roots of sensation axle, is respectively: output shaft 1 and the second outer output shaft 10 in the outer output shaft 18, second of output shaft 17, first in interior input shaft 14, outer input shaft 28, first, this six roots of sensation axle horizontal positioned.
Interior input shaft 14 and the mutually nested setting of outer input shaft 28, outer input shaft 28 is hollow shaft, and outer input shaft 28 to be set on interior input shaft 14 and coaxial with interior input shaft 14.First clutch 30 is connected with interior input shaft 14 and for controlling interior input shaft 14, and second clutch 31 is connected with outer input shaft 28 and for controlling outer input shaft 28.
Output shaft 17 and the mutually nested setting of the first outer output shaft 18 in first, the first outer output shaft 18 is hollow shaft, the first outer output shaft 18 to be set in first on output shaft 17 and with first in output shaft 17 coaxial.
Output shaft 1 and the mutually nested setting of the second outer output shaft 10 in second, the second outer output shaft 10 is hollow shaft, the second outer output shaft 10 to be set in second on output shaft 1 and with second in output shaft 1 coaxial.In interior input shaft 14, first, in output shaft 17 and second, output shaft 1 is parallel to each other layout.
Interior input shaft 14 is provided with ten grades of driving gears 11, six grades of driving gears 12, fourth gear driving gear 15 and second gear driving gears 13 successively near motor one end.Outer input shaft 28 is provided with seven grades of driving gears, 34, nine grades of driving gears 32 and third speed drive gear 33 successively near motor one end.
In first, output shaft 17 and the first outer output shaft 18 are provided with the first final gear 26, nine grades of driven gears 27, the 6th synchronizer 25, third gear driven gear 22, ten grades of driven gears 21, the 5th synchronizer 20, fourth gear driven gear 19 and the 4th synchronizer 16 successively near motor one end.Wherein, first final gear 26, nine grades driven gear 27 and the 4th synchronizer 16 are arranged in first on output shaft 17, and the 6th synchronizer 25, third gear driven gear 22, ten grades of driven gears 21, the 5th synchronizer 20 and fourth gear driven gear 19 are arranged on the first outer output shaft 18.
In second, output shaft 1 and the second outer output shaft 10 are provided with the second final gear 2, seven grades of driven gear 3, first synchronizers 4, reverse driving gear 5, second synchronizer 6, six grades of driven gears 7, the 3rd synchronizer 8 and second gear driven gear 9 successively near motor one end.Wherein, second final gear 2, seven grades driven gear 3 and the first synchronizer 4 are arranged in second on output shaft 1, and reverse driving gear 5, second synchronizer 6, six grades of driven gears 7, the 3rd synchronizer 8 and second gear driven gear 9 are arranged on the second outer output shaft 10.
Second gear driving gear 13 often engages with second gear driven gear 9, third speed drive gear 33 often engages with third gear driven gear 22, fourth gear driving gear 15 often engages with fourth gear driven gear 19, six grades of driving gears 12 often engage with six grades of driven gears 7, seven grades of driving gears 34 often engage with seven grades of driven gears 3, nine grades of driving gears 32 often engage with nine grades of driven gears 27, and ten grades of driving gears 11 often engage with ten grades of driven gears 21, and reverse driving gear 5 often engages with third gear driven gear 22, each gear on interior input shaft 14 and outer input shaft 28 is all by welding, spline, the modes such as interference press-fits are fixed on corresponding axle or are directly formed on the axle of correspondence, output shaft 17 in first, first outer output shaft 18, in second on output shaft 1 and the second outer output shaft 10 except each gear of the first final gear 26 except the second final gear 2 all by bearing empty set on corresponding axle, first final gear 26 to be fixed in first on output shaft 17, second final gear 2 to be fixed in second on output shaft 1, the tooth hub of each synchronizer all by spline joint on the axle of correspondence.
Third speed drive gear 33 and reverse driving gear 5 simultaneously with third gear driven gear 22 for often to engage, and be co-planar gear set.First final gear 26 and the second final gear 2 simultaneously with differential mechanism gear ring 24 for often to engage, and be co-planar gear set.
First synchronizer 4 can engage with seven grades of driven gears 3 and the second outer output shaft 10.In the present embodiment, second synchronizer 6 can engage with reverse driving gear 5 and six grades of driven gears 7,3rd synchronizer 8 can engage with second gear driven gear 9, but not as limit, also can be set in other embodiments: the second synchronizer 6 can engage with reverse driving gear 5, the 3rd synchronizer 8 can engage with six grades of driven gears 7 and second gear driven gear 9.4th synchronizer 16 can engage with the first outer output shaft 18.5th synchronizer 20 can engage with fourth gear driven gear 19 and ten grades of driven gears 21.6th synchronizer 25 can engage with nine grades of driven gears 27 and third gear driven gear 22.Particularly, the first outer output shaft 18 is provided with the first joining portion the 35, four synchronizer 16 and can engages with the first joining portion 35 in the one end away from motor; Second outer output shaft 10 is provided with the second joining portion 36, first synchronizer 4 and can engages with the second joining portion 36 in the one end being close to motor.By the joint of the 4th synchronizer 16 and the first outer output shaft 18, power can be realized and transmit between output shaft 17 in the first outer output shaft 18 and first; By the joint of the first synchronizer 4 and the second outer output shaft 10, power can be realized and transmit between output shaft 1 in the second outer output shaft 10 and second.
Each axle all by bearings in case of transmission (not shown), gear on each axle and synchronizer are perpendicular to the direction of axle being arranged in order and setting of substantially aliging, such as, second gear driven gear 9, second gear driving gear 13 and the 4th synchronizer 16 substantially align setting, 3rd synchronizer 8, fourth gear driving gear 15 and fourth gear driven gear 19 substantially align setting, six grades of driven gears 7, six grades of driving gears 12 and the 5th synchronizer 20 substantially align setting, all the other are similar, arrange like this and structure can be made to become compacter and the axial length effectively shortening speed changer.
Operationally each shelves power transmission is as follows for the automatic transmission of the present embodiment:
One grade of power transmission route: the 6th synchronizer 25 and third gear driven gear 22 engage, the 5th synchronizer 20 and fourth gear driven gear 19 engage, and the 3rd synchronizer 8 and second gear driven gear 9 engage, and the first synchronizer 4 and the second outer output shaft 10 engage.Second clutch 31 closes, Engine torque passes to the third speed drive gear 33 on outer input shaft 28 by second clutch 31, third gear driven gear 22 is passed to via third speed drive gear 33, the 5th synchronizer 20 is transferred torque to by the joint of third gear driven gear 22 and the 6th synchronizer 25, transfer torque on interior input shaft 14 by the 5th synchronizer 20 with the joint of fourth gear driven gear 19, second gear driven gear 9 is delivered to again by the second gear driving gear 13 on interior input shaft 14, the second outer output shaft 10 is transferred torque to by the joint of second gear driven gear 9 and the 3rd synchronizer 8, the second final gear 2 in second on output shaft 1 is transferred torque to again by the joint of the second outer output shaft 10 and the first synchronizer 4, again by differential mechanism gear ring 24, and it is final by differential mechanism 23 outputting power.
Second gear power transmission route: the 3rd synchronizer 8 and second gear driven gear 9 engage, the first synchronizer 4 and the second outer output shaft 10 engage.First clutch 30 closes, Engine torque passes to interior input shaft 14 by first clutch 30, second gear driven gear 9 is passed to via the second gear driving gear 13 be fixed on interior input shaft 14, transfer torque on the second outer output shaft 10 by the joint of second gear driven gear 9 and the 3rd synchronizer 8 again, the second final gear 2 in second on output shaft 1 is transferred torque to again by the joint of the second outer output shaft 10 and the first synchronizer 4, again by differential mechanism gear ring 24, and final by differential mechanism 23 outputting power.
Third gear power transmission route: the 6th synchronizer 25 and third gear driven gear 22 engage, the 4th synchronizer 16 and the first outer output shaft 18 engage.Second clutch 31 closes, Engine torque passes to the third speed drive gear 33 on outer input shaft 28 by second clutch 31, third gear driven gear 22 is passed to via third speed drive gear 33, transfer torque on the first outer output shaft 18 by the joint of third gear driven gear 22 and the 6th synchronizer 25, the first final gear 26 in first on output shaft 17 is transferred torque to again by the joint of the first outer output shaft 18 and the 4th synchronizer 16, again by differential mechanism gear ring 24, and final by differential mechanism 23 outputting power.
Fourth gear power transmission route: the 5th synchronizer 20 and fourth gear driven gear 19 engage, the 4th synchronizer 16 and the first outer output shaft 18 engage.First clutch 30 closes, Engine torque passes to interior input shaft 14 by first clutch 30, fourth gear driven gear 19 is passed to via the fourth gear driving gear 15 be fixed on interior input shaft 14, transfer torque on the first outer output shaft 18 by the joint of fourth gear driven gear 19 and the 5th synchronizer 20 again, the first final gear 26 in first on output shaft 17 is transferred torque to again by the joint of the first outer output shaft 18 and the 4th synchronizer 16, again by differential mechanism gear ring 24, and final by differential mechanism 23 outputting power.
Five grades of power transmission routes: the 6th synchronizer 25 and third gear driven gear 22 engage, the 5th synchronizer 20 and fourth gear driven gear 19 engage, and the second synchronizer 6 and six grades of driven gears 7 engage, and the first synchronizer 4 and the second outer output shaft 10 engage.Second clutch 31 closes, Engine torque passes to the third speed drive gear 33 on outer input shaft 28 by second clutch 31, third gear driven gear 22 is passed to via third speed drive gear 33, the 5th synchronizer 20 on the first outer output shaft 18 is transferred torque to by the joint of third gear driven gear 22 and the 6th synchronizer 25, to be transferred torque to six grades of driving gears 12 on interior input shaft 14 again with the joint of fourth gear driven gear 19 by the 5th synchronizer 20, six grades of driving gears 12 transfer torque to six grades of driven gears 7, transfer torque on the second outer output shaft 10 by the joint of six grades of driven gears 7 and the second synchronizer 6, the second final gear 2 in second on output shaft 1 is transferred torque to again by the joint of the second outer output shaft 10 and the first synchronizer 4, again by differential mechanism gear ring 24, and it is final by differential mechanism 23 outputting power.
Six grades of power transmission routes: the second synchronizer 6 and six grades of driven gears 7 engage, the first synchronizer 4 and the second outer output shaft 10 engage.First clutch 30 closes, Engine torque passes to interior input shaft 14 by first clutch 30, six grades of driven gears 7 are passed to via the six grades of driving gears 12 be fixed on interior input shaft 14, transfer torque on the second outer output shaft 10 by the joint of six grades of driven gears 7 and the second synchronizer 6 again, the second final gear 2 in second on output shaft 1 is transferred torque to again by the joint of the second outer output shaft 10 and the first synchronizer 4, again by differential mechanism gear ring 24, and final by differential mechanism 23 outputting power.
Seven grades of power transmission routes: the first synchronizer 4 and seven grades of driven gears 3 engage.Second clutch 31 closes, Engine torque passes to seven grades of driving gears 34 on outer input shaft 28 by second clutch 31, seven grades of driving gears 34 transfer torque to seven grades of driven gears 3, the second final gear 2 in second on output shaft 1 is transferred torque to by the joint of seven grades of driven gears 3 and the first synchronizer 4, again by differential mechanism gear ring 24, and final by differential mechanism 23 outputting power.
Eight grades of power transmission routes: the 5th synchronizer 20 and ten grades of driven gears 21 engage, the 6th synchronizer 25 and nine grades of driven gears 27 engage, and the first synchronizer 4 and seven grades of driven gears 3 engage.First clutch 30 closes, Engine torque passes to ten grades of driving gears 11 on interior input shaft 14 by first clutch 30, ten grades of driving gears 11 transfer torque to ten grades of driven gears 21, the 6th synchronizer 25 on the first outer output shaft 18 is transferred torque to by the joint of ten grades of driven gears 21 and the 5th synchronizer 20, seven grades of driving gears 34 on outer input shaft 28 are transferred torque to again by the joint of the 6th synchronizer 25 and nine grades of driven gears 27, seven grades of driving gears 34 transfer torque to seven grades of driven gears 3, the second final gear 2 in second on output shaft 1 is transferred torque to again by the joint of seven grades of driven gears 3 and the first synchronizer 4, again by differential mechanism gear ring 24, and it is final by differential mechanism 23 outputting power.
Nine grades of power transmission routes: the 6th synchronizer 25 and nine grades of driven gears 27 engage, the 4th synchronizer 16 and the first outer output shaft 18 engage.Second clutch 31 closes, Engine torque passes to nine grades of driving gears 32 on outer input shaft 28 by second clutch 31, nine grades of driving gears 32 transfer torque to nine grades of driven gears 27, transfer torque on the first outer output shaft 18 by the joint of nine grades of driven gears 27 and the 6th synchronizer 25, the first final gear 26 in first on output shaft 17 is transferred torque to again by the joint of the first outer output shaft 18 and the 4th synchronizer 16, again by differential mechanism gear ring 24, and final by differential mechanism 23 outputting power.
Ten grades of power transmission routes: the 5th synchronizer 20 and ten grades of driven gears 21 engage, the 4th synchronizer 16 and the first outer output shaft 18 engage.First clutch 30 closes, Engine torque passes to interior input shaft 14 by first clutch 30, ten grades of driven gears 21 are passed to via the ten grades of driving gears 11 be fixed on interior input shaft 14, transfer torque on the first outer output shaft 18 by the joint of ten grades of driven gears 21 and the 5th synchronizer 20, the first final gear 26 in first on output shaft 17 is transferred torque to again by the joint of the first outer output shaft 18 and the 4th synchronizer 16, again by differential mechanism gear ring 24, and final by differential mechanism 23 outputting power.
Reverse gear power transmission route: the 3rd synchronizer 8 and second gear driven gear 9 engage, the second synchronizer 6 and reverse driving gear 5 engage, and the 4th synchronizer 16 and the first outer output shaft 18 engage, and the 6th synchronizer 25 and third gear driven gear 22 engage.First clutch 30 closes, Engine torque passes to the second gear driving gear 13 on interior input shaft 14 by first clutch 30, second gear driving gear 13 transfers torque to second gear driven gear 9, the second synchronizer 6 on the second outer output shaft 10 is transferred torque to by the joint of second gear driven gear 9 and the 3rd synchronizer 8, because reverse driving gear 5 often engages with third gear driven gear 22, third gear driven gear 22 is transferred torque to the joint of reverse driving gear 5 by the second synchronizer 6, joint via third gear driven gear 22 and the 6th synchronizer 25 transfers torque on the first outer output shaft 18, the first final gear 26 in first on output shaft 17 is transferred torque to again by the joint of the first outer output shaft 18 and the 4th synchronizer 16, again by differential mechanism gear ring 24, and it is final by differential mechanism 23 outputting power.
Ten fast double-clutch automatic gearboxes of the embodiment of the present invention, be applicable to being applied on front horizontal forerunner's car, it comprises interior input shaft, the outer input shaft of setting nested with interior input shaft, output shaft in first, first outer output shaft of setting nested with output shaft in first, output shaft in second, and the second outer output shaft of setting nested with output shaft in second, this automatic transmission adopts the output shaft structure of two groups of nested arrangement, realized the transmission of power by a synchronizer between two output shafts wherein often organizing nested arrangement, by using the mode of gear, achieve ten forward gears and a reverse gear, the compact axial dimension of whole gearbox designs is little, required installing space is less, structure is more simply easy to processing, with common seven, eight speed transmission can arrange ten gears under having the prerequisite of identical external dimension, it is more reasonable that velocity ratio distributes, motor is made to have more probability to be operated in its best region, improve power character and Economy.
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 (6)
1. ten fast double-clutch automatic gearboxes, is characterized in that, comprising:
Interior input shaft (14) and the outer input shaft (28) of mutually nested setting, interior input shaft (14) is provided with ten grades of driving gears (11), six grades of driving gears (12), fourth gear driving gear (15) and second gear driving gears (13) successively near motor one end, outer input shaft (28) is provided with seven grades of driving gears (34), nine grades of driving gears (32) and third speed drive gear (33) successively near motor one end;
The first clutch (30) be connected with interior input shaft (14);
The second clutch (31) be connected with outer input shaft (28);
Mutually nested setting first in output shaft (17) and the first outer output shaft (18), in first, output shaft (17) and the first outer output shaft (18) are provided with from close motor one end the first final gear (26), nine grades of driven gears (27), the 6th synchronizer (25), third gear driven gear (22), ten grades of driven gears (21), the 5th synchronizer (20), fourth gear driven gear (19) and the 4th synchronizers (16) successively; Wherein, first final gear (26), nine grades of driven gears (27) and the 4th synchronizer (16) are arranged on output shaft in first (17), and the 6th synchronizer (25), third gear driven gear (22), ten grades of driven gears (21), the 5th synchronizer (20) and fourth gear driven gears (19) are arranged on the first outer output shaft (18);
Mutually nested setting second in output shaft (1) and the second outer output shaft (10), in second, output shaft (1) and the second outer output shaft (10) are provided with from close motor one end the second final gear (2), seven grades of driven gears (3), the first synchronizer (4), reverse driving gear (5), the second synchronizer (6), six grades of driven gears (7), the 3rd synchronizer (8) and second gear driven gears (9) successively; Wherein, second final gear (2), seven grades of driven gears (3) and the first synchronizer (4) are arranged on output shaft in second (1), and reverse driving gear (5), the second synchronizer (6), six grades of driven gears (7), the 3rd synchronizer (8) and second gear driven gears (9) are arranged on the second outer output shaft (10);
Wherein, second gear driving gear (13) often engages with second gear driven gear (9), third speed drive gear (33) often engages with third gear driven gear (22), fourth gear driving gear (15) often engages with fourth gear driven gear (19), six grades of driving gears (12) are often engaged with six grades of driven gears (7), seven grades of driving gears (34) are often engaged with seven grades of driven gears (3), nine grades of driving gears (32) are often engaged with nine grades of driven gears (27), ten grades of driving gears (11) are often engaged with ten grades of driven gears (21), reverse driving gear (5) often engages with third gear driven gear (22), each gear on interior input shaft (14) and outer input shaft (28) is all fixed on corresponding axle or is directly formed on the axle of correspondence, output shaft (17) in first, first outer output shaft (18), in second on output shaft (1) and the second outer output shaft (10) except each gear equal empty set of the first final gear (26) except the second final gear (2) is on corresponding axle, first final gear (26) is fixed on output shaft in first (17), second final gear (2) is fixed on output shaft in second (1), the tooth hub of each synchronizer is all connected on corresponding axle.
2. ten fast double-clutch automatic gearboxes as claimed in claim 1, it is characterized in that: the first synchronizer (4) can engage with seven grades of driven gears (3) and the second outer output shaft (10), second synchronizer (6) can engage with reverse driving gear (5) and six grades of driven gears (7), 3rd synchronizer (8) can engage with second gear driven gear (9), 4th synchronizer (16) can engage with the first outer output shaft (18), 5th synchronizer (20) can engage with fourth gear driven gear (19) and ten grades of driven gears (21), 6th synchronizer (25) can engage with nine grades of driven gears (27) and third gear driven gear (22).
3. ten fast double-clutch automatic gearboxes as claimed in claim 1, it is characterized in that: the first synchronizer (4) can engage with seven grades of driven gears (3) and the second outer output shaft (10), second synchronizer (6) can engage with reverse driving gear (5), 3rd synchronizer (8) can engage with six grades of driven gears (7) and second gear driven gear (9), 4th synchronizer (16) can engage with the first outer output shaft (18), 5th synchronizer (20) can engage with fourth gear driven gear (19) and ten grades of driven gears (21), 6th synchronizer (25) can engage with nine grades of driven gears (27) and third gear driven gear (22).
4. ten fast double-clutch automatic gearboxes as claimed in claim 1, it is characterized in that: the first outer output shaft (18) is provided with the first joining portion (35) in the one end away from motor, the 4th synchronizer (16) can engage with the first joining portion (35).
5. ten fast double-clutch automatic gearboxes as claimed in claim 1, it is characterized in that: the second outer output shaft (10) is provided with the second joining portion (36) in the one end being close to motor, the first synchronizer (4) can engage with the second joining portion (36).
6. ten fast double-clutch automatic gearboxes as claimed in claim 1, it is characterized in that: this automatic transmission also comprises differential mechanism gear ring (24), the first final gear (26) and the second final gear (2) often engage with differential mechanism gear ring (24) simultaneously.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410436278.3A CN105443678B (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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| CN201410436278.3A CN105443678B (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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| CN105443678A true CN105443678A (en) | 2016-03-30 |
| CN105443678B CN105443678B (en) | 2018-05-11 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113685500A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
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| DE102013001567A1 (en) * | 2013-01-30 | 2014-07-31 | Daimler Ag | Double-clutch transmission for use in motor vehicle, comprises gearwheel planes and switching units which are designed for connection of the forward gears |
| DE102013002943A1 (en) * | 2013-02-21 | 2014-08-21 | Daimler Ag | Dual clutch transmission for powertrain of motor vehicle, has seven switching units that are provided to rotationally fix intermediate shaft and countershafts |
| CN204025557U (en) * | 2014-08-29 | 2014-12-17 | 广州汽车集团股份有限公司 | Ten fast double-clutch automatic gearboxes |
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| US20080293533A1 (en) * | 2007-05-21 | 2008-11-27 | General Motors Corporation | Nine or Ten Speed Split Clutch Countershaft Automatic Transmission |
| DE102011117046A1 (en) * | 2010-10-27 | 2012-05-03 | Volkswagen Aktiengesellschaft | Dual clutch winding gearbox for motor vehicle, has transmission input shafts that are loosely connected with each other by the connecting gears rotatably connected with each other and comprised of a gear stage for connection to shaft |
| FR2971572B1 (en) * | 2011-02-10 | 2014-03-14 | Pascal Thery | DOUBLE CLUTCH GEARBOX COMPRISING A TRANSFER LINK |
| US20130047760A1 (en) * | 2011-08-31 | 2013-02-28 | Honda Motor Co., Ltd. | Control system of transmission |
| DE102011083695A1 (en) * | 2011-09-29 | 2013-04-04 | Zf Friedrichshafen Ag | Transmission i.e. wet-running dual clutch transmission, for commercial vehicle, has central shaft directly connected with output shaft by switching device, and spur wheel sections provided between output shaft and solid or hollow shaft |
| CN202468867U (en) * | 2011-12-26 | 2012-10-03 | 叶文森 | Parallel planetary gear transmission twin-countershaft transmission drive axle |
| DE102013001567A1 (en) * | 2013-01-30 | 2014-07-31 | Daimler Ag | Double-clutch transmission for use in motor vehicle, comprises gearwheel planes and switching units which are designed for connection of the forward gears |
| DE102013002943A1 (en) * | 2013-02-21 | 2014-08-21 | Daimler Ag | Dual clutch transmission for powertrain of motor vehicle, has seven switching units that are provided to rotationally fix intermediate shaft and countershafts |
| CN103711845A (en) * | 2013-12-30 | 2014-04-09 | 长城汽车股份有限公司 | Multi-gear dual-clutch transmission and car |
| CN204025557U (en) * | 2014-08-29 | 2014-12-17 | 广州汽车集团股份有限公司 | Ten fast double-clutch automatic gearboxes |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113685500A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685500B (en) * | 2020-05-18 | 2024-01-26 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
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|---|---|
| CN105443678B (en) | 2018-05-11 |
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