CN204025555U - Ten fast double-clutch automatic gearboxes - Google Patents
Ten fast double-clutch automatic gearboxes Download PDFInfo
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- CN204025555U CN204025555U CN201420495494.0U CN201420495494U CN204025555U CN 204025555 U CN204025555 U CN 204025555U CN 201420495494 U CN201420495494 U CN 201420495494U CN 204025555 U CN204025555 U CN 204025555U
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Abstract
A kind of ten fast double-clutch automatic gearboxes, comprise interior input shaft, outer input shaft with the nested setting of interior input shaft, the first interior output shaft, the first outer output shaft with the nested setting of the first interior output shaft, the second interior output shaft, and with the second outer output shaft of the nested setting of the second interior output shaft, this automatic transmission adopts the output shaft structure of two groups of nested arrangement, wherein between two of every group of nested arrangement output shafts, realize the transmission of power by a synchronizer, by using the mode of gear, having realized ten forward gears and one reverses 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 gear speed transmissions have under the prerequisite of identical external dimension can arrange ten gears, it is more reasonable that velocity ratio distributes, make motor have more probability to be operated in its best region, improve power character and Economy.
Description
Technical field
The utility model relates to the speed changer technical field of vehicle, relates in particular to a kind of ten fast double-clutch automatic gearboxes.
Background technique
Double-clutch automatic gearbox (Dual Clutch Transmission, DCT) be 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 gear shifting of shift process, interrupt power at shift process, overcome electric-controlled mechanical automatic speed transmission (Automated Mechanical Transmission, AMT) shortcoming that gearshift is impacted, vehicle is in shift process, the power of motor can be delivered to wheel all the time, gearshift rapidly steadily, not only ensure the acceleration of vehicle, and because vehicle no longer produces the abrupt deceleration situation causing due to gearshift, also improved greatly the travelling comfort of vehicle operating.
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 front transverse engine, front-wheel drive such vehicle, particularly compact car, because its installing space is restricted, above-mentioned speed changer is more difficult employing just, and because the gear of its speed change is less, 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 have a negative impact.
Model utility content
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 gears that advance, velocity ratio is distributed more reasonable.
Embodiment of the present utility model provides a kind of ten fast double-clutch automatic gearboxes, comprising:
The interior input shaft of mutually nested setting and outer input shaft, on interior input shaft, from eight gear driving gears, six gear driving gears, four gear driving gears and two gear driving gears are installed successively near motor one end, nine gear driving gears, seven gear driving gears and three gear driving gears are installed from close motor one end on outer input shaft successively;
The first clutch being connected with interior input shaft;
The second clutch being connected with outer input shaft;
The first interior output shaft of mutually nested setting and the first outer output shaft, keep off driven gears, the 6th synchronizer, three gear driven gears, eight gear driven gears, the 5th synchronizer, four gear driven gear and the 4th synchronizers from the first final gear, seven is installed successively near motor one end on the first interior output shaft and the first outer output shaft; Wherein, the first final gear, seven gear driven gears and the 4th synchronizer are arranged on the first interior output shaft, and the 6th synchronizer, three gear driven gears, eight gear driven gears, the 5th synchronizer and four gear driven gears are arranged on the first outer output shaft;
The second interior output shaft of mutually nested setting and the second outer output shaft, keep off driven gears, the first synchronizer, the driving gear that reverses gear, the second synchronizer, six gear driven gears, the 3rd synchronizer and two gear driven gears from the second final gear, nine is installed successively near motor one end on the second interior output shaft and the second outer output shaft; Wherein, the second final gear, nine gear driven gears and the first synchronizer are arranged on the second interior output shaft, and the driving gear that reverses gear, the second synchronizer, six gear driven gears, the 3rd synchronizer and two gear driven gears are arranged on the second outer output shaft;
Wherein, two gear driving gears often engage with two gear driven gears, three gear driving gears often engage with three gear driven gears, four gear driving gears often engage with four gear driven gears, six gear driving gears often engage with six gear driven gears, and seven gear driving gears often engage with seven gear driven gears, and eight gear driving gears often engage with eight gear driven gears, nine gear driving gears often engage with nine gear driven gears, and the driving gear that reverses gear often engages with three gear driven gears; Each gear on interior input shaft and outer input shaft is all fixed on corresponding axle or directly and forms on corresponding axle, on the first interior output shaft, the first outer output shaft, the second interior output shaft and the second outer output shaft except the first final gear with the equal empty set of each gear the second final gear on corresponding axle, the first final gear is fixed on the first interior output shaft, the second final gear is fixed on the second interior output shaft, and the tooth hub of each synchronizer is all connected on corresponding axle.
Further, the first synchronizer can engage with nine gear driven gears and the second outer output shaft, the second synchronizer can engage with reverse gear driving gear and six gear driven gears, the 3rd synchronizer can engage with two gear driven gears, the 4th synchronizer can engage with the first outer output shaft, the 5th synchronizer can engage with four gear driven gears and eight gear driven gears, and the 6th synchronizer can engage with seven gear driven gears and three gear driven gears.
Further, the first synchronizer can engage with nine gear driven gears and the second outer output shaft, the second synchronizer can engage with the driving gear that reverses gear, the 3rd synchronizer can engage with six gear driven gears and two gear driven gears, the 4th synchronizer can engage with the first outer output shaft, the 5th synchronizer can engage with four gear driven gears and eight gear driven gears, and the 6th synchronizer can engage with seven gear driven gears and three gear driven gears.
Further, the first outer output shaft is in being provided with the first joining portion away from one end of 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 that relies on 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, wherein between two of every group of nested arrangement output shafts, realize the transmission of power by a synchronizer, by using the mode of gear, having realized ten forward gears and one reverses 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 gear speed transmissions have under the prerequisite of identical external dimension can arrange ten gears, it is more reasonable that velocity ratio distributes, make motor have more probability to be operated in its best region, improve power character and Economy.
Brief description of the drawings
Fig. 1 is the structural representation of the utility model embodiment's ten fast double-clutch automatic gearboxes.
Embodiment
The utility model provides a kind of ten fast double-clutch automatic gearboxes, particularly a kind of ten fast double-clutch automatic gearboxes that are applicable to front transverse engine, forerunner's car, the problems such as large, the required installing space of axial length for existing double-clutch automatic gearbox is large, velocity ratio is difficult for distributing, gear number is few, provide that little, the required installing space of a kind of axial length is less, velocity ratio distributes rationally, ten more fast double-clutch automatic gearboxes of gear number.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.
Fig. 1 is the structural representation of the utility model embodiment's ten fast double-clutch automatic gearboxes, please refer to the drawing 1, the automatic transmission of the present embodiment comprises: the second interior output shaft 1, the second final gear 2, nine gear driven gears 3, the first synchronizer 4, driving gear 5 reverses gear, the second synchronizer 6, six gear driven gears 7, the 3rd synchronizer 8, two gear driven gears 9, the second outer output shaft 10, eight gear driving gears 11, six gear driving gears 12, two gear driving gears 13, interior input shaft 14, four gear driving gears 15, the 4th synchronizer 16, the first interior output shaft 17, the first outer output shaft 18, four gear driven gears 19, the 5th synchronizer 20, eight gear driven gears 21, three gear driven gears 22, differential mechanism 23, differential mechanism gear ring 24, the 6th synchronizer 25, the first final gear 26, seven gear driven gears 27, outer input shaft 28, motor 29, first clutch 30, second clutch 31, seven gear driving gears 32, three gear driving gears 33 and nine gear driving gears 34.
This automatic transmission comprises six roots of sensation axle, is respectively: interior input shaft 14, outer input shaft 28, the first interior output shaft 17, the first outer output shaft 18, the second interior output shaft 1 and the second outer output shaft 10, 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, outer input shaft 28 is set on interior input shaft 14 and is 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.
The first interior output shaft 17 and the mutually nested setting of the first outer output shaft 18, the first outer output shaft 18 is hollow shaft, the first outer output shaft 18 is set on the first interior output shaft 17 and is coaxial with the first interior output shaft 17.
The second interior output shaft 1 and the mutually nested setting of the second outer output shaft 10, the second outer output shaft 10 is hollow shaft, the second outer output shaft 10 is set on the second interior output shaft 1 and is coaxial with the second interior output shaft 1.Interior input shaft 14, the first interior output shaft 17 and the second interior output shaft 1 layout that is parallel to each other.
Eight gear driving gears 11, six gear driving gears 12, four gear driving gears 15 and two gear driving gears 13 are installed successively on interior input shaft 14 from close motor one end.Nine gear driving gears 34, seven gear driving gears 32 and three gear driving gears 33 are installed successively on outer input shaft 28 from close motor one end.
The first final gear 26, seven gear driven gears 27, the 6th synchronizer 25, three gear driven gears 22, eight gear driven gears 21, the 5th synchronizer 20, four gear driven gear 19 and the 4th synchronizers 16 are installed successively on the first interior output shaft 17 and the first outer output shaft 18 from close motor one end.Wherein, the first final gear 26, seven gear driven gears 27 and the 4th synchronizer 16 are arranged on the first interior output shaft 17, and the 6th synchronizer 25, three gear driven gears 22, eight gear driven gears 21, the 5th synchronizer 20 and four gear driven gears 19 are arranged on the first outer output shaft 18.
On the second interior output shaft 1 and the second outer output shaft 10 from the second final gear 2, nine gear driven gear 3, the first synchronizers 4 are installed successively near motor one end, driving gear 5, the second synchronizer 6, six gear driven gears 7, the 3rd synchronizer 8 and two gear driven gears 9 reverse gear.Wherein, the second final gear 2, nine gear driven gears 3 and the first synchronizer 4 are arranged on the second interior output shaft 1, and reverse gear driving gear 5, the second synchronizer 6, six gear driven gears 7, the 3rd synchronizer 8 and two gear driven gears 9 are arranged on the second outer output shaft 10.
Two gear driving gears 13 often engage with two gear driven gears 9, three gear driving gears 33 often engage with three gear driven gears 22, four gear driving gears 15 often engage with four gear driven gears 19, six gear driving gears 12 often engage with six gear driven gears 7, seven gear driving gears 32 often engage with seven gear driven gears 27, eight gear driving gears 11 often engage with eight gear driven gears 21, and nine gear driving gears 34 often engage with nine gear driven gears 3, and the driving gear 5 that reverses gear often engages with three gear driven gears 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 directly and form on corresponding axle, the first interior output shaft 17, the first outer output shaft 18, on the second interior output shaft 1 and the second outer output shaft 10 except the first final gear 26 and each gear the second final gear 2 all by bearing empty set on corresponding axle, the first final gear 26 is fixed on the first interior output shaft 17, the second final gear 2 is fixed on the second interior output shaft 1, the tooth hub of each synchronizer all by spline joint on corresponding axle.
Three gear driving gears 33 and the driving gear 5 of reversing gear simultaneously with three gear driven gears 22 for often to engage, and be co-planar gear set.The 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.
The first synchronizer 4 can engage with nine gear driven gears 3 and the second outer output shaft 10.In the present embodiment, the second synchronizer 6 can engage with reverse gear driving gear 5 and six gear driven gears 7, the 3rd synchronizer 8 can engage with two gear driven gears 9, but not as limit, also can be set in other embodiments: the second synchronizer 6 can engage with the driving gear 5 that reverses gear, the 3rd synchronizer 8 can engage with six gear driven gears 7 and two gear driven gears 9.The 4th synchronizer 16 can engage with the first outer output shaft 18.The 5th synchronizer 20 can engage with four gear driven gears 19 and eight gear driven gears 21.The 6th synchronizer 25 can engage with seven gear driven gears 27 and three gear driven gears 22.Particularly, the first outer output shaft 18 can engage with the first joining portion 35 in be provided with the first joining portion 35, the four synchronizers 16 away from one end of motor; The second outer output shaft 10 is provided with the second joining portion 36, the first synchronizers 4 and can engages with the second joining portion 36 in the one end that relies on motor.By engaging of the 4th synchronizer 16 and the first outer output shaft 18, can realize power and transmit between the first outer output shaft 18 and the first interior output shaft 17; By engaging of the first synchronizer 4 and the second outer output shaft 10, can realize power and transmit between the second outer output shaft 10 and the second interior output shaft 1.
Each axle all by bearings in case of transmission (not shown), gear on each axle and synchronizer are arranged in order and are basic alignment setting in the direction perpendicular to axle, for example, two gear driven gears 9, two gear driving gears 13 and the 4th synchronizer 16 are basic alignment setting, the 3rd synchronizer 8, four gear driving gears 15 and four gear driven gears 19 are basic alignment setting, six gear driven gears 7, six gear driving gears 12 and the 5th synchronizer 20 are basic alignment setting, all the other are similar, the axial length that can make structure become compacter and effectively shorten speed changer is set like this.
The automatic transmission of the present embodiment each gear power transmission in the time of work is as follows:
One gear power transmission route: the 6th synchronizer 25 and three gear driven gears 22 engage, the 5th synchronizer 20 and four gear driven gears 19 engage, and the 3rd synchronizer 8 and two gear driven gears 9 engage, and the first synchronizer 4 and the second outer output shaft 10 engage.Second clutch 31 closures, Engine torque passes to the gear of three on outer input shaft 28 driving gear 33 by second clutch 31, pass to three gear driven gears 22 via three gear driving gears 33, transfer torque to the 5th synchronizer 20 by three gear driven gears 22 and engaging of the 6th synchronizer 25, transferred torque on interior input shaft 14 with four engaging of driven gear 19 of gear by the 5th synchronizer 20, be delivered to two gear driven gears 9 by the gear of two on interior input shaft 14 driving gear 13 again, transfer torque to the second outer output shaft 10 by two gear driven gears 9 and engaging of the 3rd synchronizer 8, transfer torque to the second final gear 2 on the second interior output shaft 1 by the second outer output shaft 10 and engaging of the first synchronizer 4 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Two gear power transmission routes: the 3rd synchronizer 8 and two gear driven gears 9 engage, and the first synchronizer 4 and the second outer output shaft 10 engage.First clutch 30 closures, Engine torque passes to interior input shaft 14 by first clutch 30, pass to two gear driven gears 9 via being fixed on the gear of two on interior input shaft 14 driving gear 13, transferred torque on the second outer output shaft 10 by two gear driven gears 9 and engaging of the 3rd synchronizer 8 again, transfer torque to the second final gear 2 on the second interior output shaft 1 by the second outer output shaft 10 and engaging of the first synchronizer 4 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Three gear power transmission routes: the 6th synchronizer 25 and three gear driven gears 22 engage, and the 4th synchronizer 16 and the first outer output shaft 18 engage.Second clutch 31 closures, Engine torque passes to the gear of three on outer input shaft 28 driving gear 33 by second clutch 31, pass to three gear driven gears 22 via three gear driving gears 33, transferred torque on the first outer output shaft 18 by the joint of three gear driven gears 22 and the 6th synchronizer 25, transfer torque to the first final gear 26 on the first interior output shaft 17 by the first outer output shaft 18 and engaging of the 4th synchronizer 16 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Four gear power transmission routes: the 5th synchronizer 20 and four gear driven gears 19 engage, and the 4th synchronizer 16 and the first outer output shaft 18 engage.First clutch 30 closures, Engine torque passes to interior input shaft 14 by first clutch 30, pass to four gear driven gears 19 via being fixed on the gear of four on interior input shaft 14 driving gear 15, transferred torque on the first outer output shaft 18 by four gear driven gears 19 and engaging of the 5th synchronizer 20 again, transfer torque to the first final gear 26 on the first interior output shaft 17 by the first outer output shaft 18 and engaging of the 4th synchronizer 16 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Five gear power transmission routes: the 6th synchronizer 25 and three gear driven gears 22 engage, the 5th synchronizer 20 and four gear driven gears 19 engage, and the second synchronizer 6 and six gear driven gears 7 engage, and the first synchronizer 4 and the second outer output shaft 10 engage.Second clutch 31 closures, Engine torque passes to the gear of three on outer input shaft 28 driving gear 33 by second clutch 31, pass to three gear driven gears 22 via three gear driving gears 33, transfer torque to the 5th synchronizer 20 on the first outer output shaft 18 by the joint of three gear driven gears 22 and the 6th synchronizer 25, transfer torque to the gear of six on interior input shaft 14 driving gear 12 by the 5th synchronizer 20 and engaging of four gear driven gears 19 again, six gear driving gears 12 transfer torque to six gear driven gears 7, transferred torque on the second outer output shaft 10 by six gear driven gears 7 and engaging of the second synchronizer 6, transfer torque to the second final gear 2 on the second interior output shaft 1 by the second outer output shaft 10 and engaging of the first synchronizer 4 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Six gear power transmission routes: the second synchronizer 6 and six gear driven gears 7 engage, and the first synchronizer 4 and the second outer output shaft 10 engage.First clutch 30 closures, Engine torque passes to interior input shaft 14 by first clutch 30, pass to six gear driven gears 7 via being fixed on the gear of six on interior input shaft 14 driving gear 12, transferred torque on the second outer output shaft 10 by six gear driven gears 7 and engaging of the second synchronizer 6 again, transfer torque to the second final gear 2 on the second interior output shaft 1 by the second outer output shaft 10 and engaging of the first synchronizer 4 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Seven gear power transmission routes: the 6th synchronizer 25 and seven gear driven gears 27 engage, and the 4th synchronizer 16 and the first outer output shaft 18 engage.Second clutch 31 closures, Engine torque passes to the gear of seven on outer input shaft 28 driving gear 32 by second clutch 31, seven gear driving gears 32 transfer torque to seven gear driven gears 27, transferred torque on the first outer output shaft 18 by the joint of seven gear driven gears 27 and the 6th synchronizer 25, transfer torque to the first final gear 26 on the first interior output shaft 17 by the first outer output shaft 18 and engaging of the 4th synchronizer 16 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Eight gear power transmission routes: the 5th synchronizer 20 and eight gear driven gears 21 engage, and the 4th synchronizer 16 and the first outer output shaft 18 engage.First clutch 30 closures, Engine torque passes to interior input shaft 14 by first clutch 30, pass to eight gear driven gears 21 via being fixed on the gear of eight on interior input shaft 14 driving gear 11, transferred torque on the first outer output shaft 18 by eight gear driven gears 21 and engaging of the 5th synchronizer 20, transfer torque to the first final gear 26 on the first interior output shaft 17 by the first outer output shaft 18 and engaging of the 4th synchronizer 16 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Nine gear power transmission routes: the first synchronizer 4 and nine gear driven gears 3 engage.Second clutch 31 closures, Engine torque passes to the gear of nine on outer input shaft 28 driving gear 34 by second clutch 31, nine gear driving gears 34 transfer torque to nine gear driven gears 3, transfer torque to the second final gear 2 on the second interior output shaft 1 by the joint of nine gear driven gears 3 and the first synchronizer 4, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
Ten gear power transmission routes: the 5th synchronizer 20 and eight gear driven gears 21 engage, the 6th synchronizer 25 and seven gear driven gears 27 engage, and the first synchronizer 4 and nine gear driven gears 3 engage.First clutch 30 closures, Engine torque passes to the gear of eight on interior input shaft 14 driving gear 11 by first clutch 30, eight gear driving gears 11 transfer torque to eight gear driven gears 21, transfer torque to the 6th synchronizer 25 on the first outer output shaft 18 by the joint of eight gear driven gears 21 and the 5th synchronizer 20, transfer torque to the gear of nine on outer input shaft 28 driving gear 34 by the 6th synchronizer 25 and engaging of seven gear driven gears 27 again, nine gear driving gears 34 transfer torque to nine gear driven gears 3, transfer torque to the second final gear 2 on the second interior output shaft 1 by nine gear driven gears 3 and engaging of the first synchronizer 4 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
The power transmission of reversing gear route: the 3rd synchronizer 8 and two gear driven gears 9 engage, and the second synchronizer 6 and the driving gear 5 that reverses gear engage, and the 4th synchronizer 16 and the first outer output shaft 18 engage, the 6th synchronizer 25 and three gear driven gears 22 engage.First clutch 30 closures, Engine torque passes to the gear of two on interior input shaft 14 driving gear 13 by first clutch 30, two gear driving gears 13 transfer torque to two gear driven gears 9, transfer torque to the second synchronizer 6 on the second outer output shaft 10 by the joint of two gear driven gears 9 and the 3rd synchronizer 8, owing to reversing gear, driving gear 5 often engages with three gear driven gears 22, transfer torque to three gear driven gears 22 by the second synchronizer 6 with the engaging of driving gear 5 of reversing gear, transfer torque on the first outer output shaft 18 via three gear driven gears 22 and engaging of the 6th synchronizer 25, transfer torque to the first final gear 26 on the first interior output shaft 17 by the first outer output shaft 18 and engaging of the 4th synchronizer 16 again, again by differential mechanism gear ring 24, and finally by differential mechanism 23 outputting powers.
The utility model embodiment's ten fast double-clutch automatic gearboxes, be applicable to being applied on front horizontal forerunner's car, it comprises interior input shaft, outer input shaft with the nested setting of interior input shaft, the first interior output shaft, the first outer output shaft with the nested setting of the first interior output shaft, the second interior output shaft, and with the second outer output shaft of the nested setting of the second interior output shaft, this automatic transmission adopts the output shaft structure of two groups of nested arrangement, wherein between two of every group of nested arrangement output shafts, realize the transmission of power by a synchronizer, by using the mode of gear, having realized ten forward gears and one reverses 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 gear speed transmissions have under the prerequisite of identical external dimension can arrange ten gears, it is more reasonable that velocity ratio distributes, make motor 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 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 (6)
1. ten fast double-clutch automatic gearboxes, is characterized in that, comprising:
The interior input shaft (14) of mutually nested setting and outer input shaft (28), interior input shaft (14) is upper from eight gear driving gears (11), six gear driving gears (12), four gear driving gears (15) and two gear driving gears (13) are installed successively near motor one end, and outer input shaft (28) is upper from nine gear driving gears (34), seven gear driving gears (32) and three gear driving gears (33) are installed successively near motor one end;
The first clutch (30) being connected with interior input shaft (14);
The second clutch (31) being connected with outer input shaft (28);
The first interior output shaft (17) of mutually nested setting and the first outer output shaft (18), the first interior output shaft (17) and the first outer output shaft (18) are upper from the first final gear (26), seven gear driven gear (27), the 6th synchronizers (25), three gear driven gears (22), eight gear driven gear (21), the 5th synchronizers (20), four gear driven gear (19) and the 4th synchronizers (16) are installed successively near motor one end; Wherein, it is upper that the first final gear (26), seven gear driven gears (27) and the 4th synchronizer (16) are arranged on the first interior output shaft (17), and the 6th synchronizer (25), three gear driven gears (22), eight gear driven gears (21), the 5th synchronizer (20) and four gear driven gears (19) are arranged on the first outer output shaft (18);
The second interior output shaft (1) of mutually nested setting and the second outer output shaft (10), the second interior output shaft (1) and the second outer output shaft (10) are upper from the second final gear (2), nine gear driven gear (3), the first synchronizers (4), the driving gear that reverses gear (5), the second synchronizer (6), six gear driven gears (7), the 3rd synchronizer (8) and two gear driven gears (9) are installed successively near motor one end; Wherein, it is upper that the second final gear (2), nine gear driven gears (3) and the first synchronizer (4) are arranged on the second interior output shaft (1), and the driving gear that reverses gear (5), the second synchronizer (6), six gear driven gears (7), the 3rd synchronizer (8) and two gear driven gears (9) are arranged on the second outer output shaft (10);
Wherein, two gear driving gears (13) often engage with two gear driven gears (9), three gear driving gears (33) often engage with three gear driven gears (22), four gear driving gears (15) often engage with four gear driven gears (19), six gear driving gears (12) often engage with six gear driven gears (7), seven gear driving gears (32) often engage with seven gear driven gears (27), eight gear driving gears (11) often engage with eight gear driven gears (21), nine gear driving gears (34) often engage with nine gear driven gears (3), the driving gear (5) that reverses gear often engages with three gear driven gears (22), each gear on interior input shaft (14) and outer input shaft (28) is all fixed on corresponding axle or directly and forms on corresponding axle, the first interior output shaft (17), the first outer output shaft (18), the second interior output shaft (1) and the second outer output shaft (10) upper except the first final gear (26) with the equal empty set of each gear the second final gear (2) on corresponding axle, the first final gear (26) is fixed on the first interior output shaft (17), the second final gear (2) is fixed on the second interior output shaft (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 nine gear driven gears (3) and the second outer output shaft (10), the second synchronizer (6) can engage with the driving gear that reverses gear (5) and six gear driven gears (7), the 3rd synchronizer (8) can engage with two gear driven gears (9), the 4th synchronizer (16) can engage with the first outer output shaft (18), the 5th synchronizer (20) can engage with four gear driven gears (19) and eight gear driven gears (21), the 6th synchronizer (25) can engage with seven gear driven gears (27) and three gear driven gears (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 nine gear driven gears (3) and the second outer output shaft (10), the second synchronizer (6) can engage with the driving gear that reverses gear (5), the 3rd synchronizer (8) can engage with six gear driven gears (7) and two gear driven gears (9), the 4th synchronizer (16) can engage with the first outer output shaft (18), the 5th synchronizer (20) can engage with four gear driven gears (19) and eight gear driven gears (21), the 6th synchronizer (25) can engage with seven gear driven gears (27) and three gear driven gears (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 in being provided with the first joining portion (35) away from one end of 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 that relies on 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420495494.0U CN204025555U (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420495494.0U CN204025555U (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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| CN204025555U true CN204025555U (en) | 2014-12-17 |
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| CN201420495494.0U Withdrawn - After Issue CN204025555U (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443681A (en) * | 2014-08-29 | 2016-03-30 | 广州汽车集团股份有限公司 | Ten-speed dual clutch automatic transmission |
| CN106763549A (en) * | 2016-12-30 | 2017-05-31 | 中国第汽车股份有限公司 | A kind of ten new gear double-clutch automatic transmissions |
| CN113685503A (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 |
| CN113775706A (en) * | 2020-06-10 | 2021-12-10 | 广州汽车集团股份有限公司 | Ten-speed dual-clutch transmission and vehicle |
-
2014
- 2014-08-29 CN CN201420495494.0U patent/CN204025555U/en not_active Withdrawn - After Issue
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443681A (en) * | 2014-08-29 | 2016-03-30 | 广州汽车集团股份有限公司 | Ten-speed dual clutch automatic transmission |
| CN105443681B (en) * | 2014-08-29 | 2018-10-19 | 广州汽车集团股份有限公司 | Ten fast double-clutch automatic gearboxes |
| CN106763549A (en) * | 2016-12-30 | 2017-05-31 | 中国第汽车股份有限公司 | A kind of ten new gear double-clutch automatic transmissions |
| CN106763549B (en) * | 2016-12-30 | 2023-08-25 | 中国第一汽车股份有限公司 | Novel ten-gear double-clutch type automatic transmission |
| CN113685503A (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 |
| CN113685503B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
| CN113775706A (en) * | 2020-06-10 | 2021-12-10 | 广州汽车集团股份有限公司 | Ten-speed dual-clutch transmission and vehicle |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20141217 Effective date of abandoning: 20181019 |
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| AV01 | Patent right actively abandoned |