CN204025559U - Ten fast double-clutch automatic gearboxes - Google Patents
Ten fast double-clutch automatic gearboxes Download PDFInfo
- Publication number
- CN204025559U CN204025559U CN201420497865.9U CN201420497865U CN204025559U CN 204025559 U CN204025559 U CN 204025559U CN 201420497865 U CN201420497865 U CN 201420497865U CN 204025559 U CN204025559 U CN 204025559U
- Authority
- CN
- China
- Prior art keywords
- gear
- output shaft
- synchronizer
- grades
- driven
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn - After Issue
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
Abstract
A kind of ten fast double-clutch automatic gearboxes, comprise 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.
Description
Technical field
The utility model relates to the transmission technology field of vehicle, particularly relates 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 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 (Automated Mechanical Transmission, 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.
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 advance gears, 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, interior input shaft is provided with four or six grades of driving gears, eight grades of driving gears and second gear driving gear successively near motor one end, outer input shaft is provided with seven or 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, output shaft and the first outer output shaft are provided with the first final gear, seven grades of driven gears, the 6th synchronizer, third gear driven gear, fourth gear driven gear, the 5th synchronizer, eight grades of driven gears and the 4th synchronizers successively near motor one end; Wherein, the first final gear, seven grades of driven gears and the 4th synchronizer are arranged in first on output shaft, and the 6th synchronizer, third gear driven gear, fourth gear driven gear, the 5th synchronizer and eight grades of 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, nine 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, nine 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, four or six grades of driving gears often engage with six grades of driven gears and fourth gear driven gear simultaneously, seven or nine grades of driving gears often engage with seven grades of driven gears and nine grades of driven gears simultaneously, eight grades of driving gears often engage with eight 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 nine 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 eight grades of driven gears and fourth gear driven gear, and the 6th synchronizer can engage with seven grades of driven gears and third gear driven gear.
Further, first synchronizer can engage with nine 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 eight grades of driven gears and fourth gear driven gear, and the 6th synchronizer can engage with seven 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 the ten fast double-clutch automatic gearboxes of the utility model embodiment.
Embodiment
The utility model 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 purpose of this utility model, technological scheme and advantage clearly, below in conjunction with accompanying drawing, the utility model mode of execution is further described.
Fig. 1 is the structural representation of the ten fast double-clutch automatic gearboxes of the utility model embodiment, please refer to the drawing 1, the automatic transmission of the present embodiment comprises: output shaft 1 in second, second final gear 2, nine 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, four or six grades of driving gears 12, second gear driving gear 13, interior input shaft 14, eight grades of driving gears 15, 4th synchronizer 16, output shaft 17 in first, first outer output shaft 18, eight grades of driven gears 19, 5th synchronizer 20, fourth gear driven gear 21, third gear driven gear 22, differential mechanism 23, differential mechanism gear ring 24, 6th synchronizer 25, first final gear 26, seven grades of driven gears 27, outer input shaft 28, motor 29, first clutch 30, second clutch 31, seven or nine grades of driving gears 32 and third speed drive gear 33.
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 four or six grades of driving gears, 12, eight grades of driving gears 15 and second gear driving gear 13 successively near motor one end.Outer input shaft 28 is provided with seven or 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, seven grades of driven gears 27, the 6th synchronizer 25, third gear driven gear 22, fourth gear driven gear 21, the 5th synchronizer 20, eight grades of driven gears 19 and the 4th synchronizer 16 successively near motor one end.Wherein, first final gear 26, seven 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, fourth gear driven gear 21, the 5th synchronizer 20 and eight grades of driven gears 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, nine 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, nine 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, four or six grades of driving gears 12 often engage with six grades of driven gears 7 and fourth gear driven gear 21 simultaneously, seven or nine grades of driving gears 32 often engage with seven grades of driven gears 27 and nine grades of driven gears 3 simultaneously, eight grades of driving gears 15 often engage with eight grades of driven gears 19, 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.Six grades of driven gears 7 and fourth gear driven gear 21 simultaneously with four or six grades of driving gears 12 for often to engage, and be co-planar gear set.Seven grades of driven gears 27 and nine grades of driven gears 3 simultaneously with seven or nine grades of driving gears 32 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 nine 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 eight grades of driven gears 19 and fourth gear driven gear 21.6th synchronizer 25 can engage with seven 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).
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 21 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 21, 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 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, fourth gear driven gear 21 is passed to via four or the six grades of driving gears 12 be fixed on interior input shaft 14, transfer torque on the first outer output shaft 18 by the joint of fourth gear driven gear 21 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 21 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 four or six grades of driving gears 12 on interior input shaft 14 again with the joint of fourth gear driven gear 21 by the 5th synchronizer 20, four or 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 four or 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 6th synchronizer 25 and seven 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 seven or nine grades of driving gears 32 on outer input shaft 28 by second clutch 31, seven or nine grades of driving gears 32 transfer torque to seven grades of driven gears 27, transfer torque on the first outer output shaft 18 by the joint of seven 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.
Eight grades of power transmission routes: the 5th synchronizer 20 and eight grades of driven gears 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, eight grades of driven gears 19 are passed to via the eight grades of driving gears 15 be fixed on interior input shaft 14, transfer torque on the first outer output shaft 18 by the joint of eight grades of driven gears 19 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.
Nine grades of power transmission routes: the first synchronizer 4 and nine grades of driven gears 3 engage.Second clutch 31 closes, Engine torque passes to seven or nine grades of driving gears 32 on outer input shaft 28 by second clutch 31, seven or nine grades of driving gears 32 transfer torque to nine grades of driven gears 3, the second final gear 2 in second on output shaft 1 is transferred torque to by the joint of nine 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.
Ten grades of power transmission routes: the 5th synchronizer 20 and eight grades of driven gears 19 engage, the 6th synchronizer 25 and seven grades of driven gears 27 engage, and the first synchronizer 4 and nine grades of driven gears 3 engage.First clutch 30 closes, Engine torque passes to eight grades of driving gears 15 on interior input shaft 14 by first clutch 30, eight grades of driving gears 15 transfer torque to eight grades of driven gears 19, the 6th synchronizer 25 on the first outer output shaft 18 is transferred torque to by the joint of eight grades of driven gears 19 and the 5th synchronizer 20, seven or nine grades of driving gears 32 on outer input shaft 28 are transferred torque to again by the joint of the 6th synchronizer 25 and seven grades of driven gears 27, seven or nine grades of driving gears 32 transfer torque to nine 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 nine 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.
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.
The ten fast double-clutch automatic gearboxes of the utility model embodiment, 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 utility model, not in order to limit the utility model, all within spirit of the present utility model and principle, any amendment done, equivalent replacement, improvement etc., all should be included within protection domain of the present utility model.
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 four or six grades of driving gears (12), eight grades of driving gears (15) and second gear driving gear (13) successively near motor one end, outer input shaft (28) is provided with seven or 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 the first final gear (26), seven grades of driven gears (27), the 6th synchronizer (25), third gear driven gear (22), fourth gear driven gear (21), the 5th synchronizer (20), eight grades of driven gears (19) and the 4th synchronizers (16) successively from close motor one end; Wherein, first final gear (26), seven 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), fourth gear driven gear (21), the 5th synchronizer (20) and eight grades of 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), nine 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), nine 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), four or six grades of driving gears (12) are often engaged with six grades of driven gears (7) and fourth gear driven gear (21) simultaneously, seven or nine grades of driving gears (32) are often engaged with seven grades of driven gears (27) and nine grades of driven gears (3) simultaneously, eight grades of driving gears (15) are often engaged with eight grades of driven gears (19), 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 nine 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 eight grades of driven gears (19) and fourth gear driven gear (21), 6th synchronizer (25) can engage with seven 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 nine 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 eight grades of driven gears (19) and fourth gear driven gear (21), 6th synchronizer (25) can engage with seven 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420497865.9U CN204025559U (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420497865.9U CN204025559U (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204025559U true CN204025559U (en) | 2014-12-17 |
Family
ID=52065428
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420497865.9U Withdrawn - After Issue CN204025559U (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204025559U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105370820A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Automatic ten-gear double-clutch transmission |
| CN107539090A (en) * | 2016-06-29 | 2018-01-05 | 比亚迪股份有限公司 | Power-driven system and vehicle |
| CN110836249A (en) * | 2018-08-15 | 2020-02-25 | 上海汽车集团股份有限公司 | Automobile and ten-speed transmission thereof |
-
2014
- 2014-08-29 CN CN201420497865.9U patent/CN204025559U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105370820A (en) * | 2014-08-29 | 2016-03-02 | 广州汽车集团股份有限公司 | Automatic ten-gear double-clutch transmission |
| CN107539090A (en) * | 2016-06-29 | 2018-01-05 | 比亚迪股份有限公司 | Power-driven system and vehicle |
| CN110836249A (en) * | 2018-08-15 | 2020-02-25 | 上海汽车集团股份有限公司 | Automobile and ten-speed transmission thereof |
| CN110836249B (en) * | 2018-08-15 | 2021-09-21 | 上海汽车集团股份有限公司 | Automobile and ten-speed transmission thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP4855092B2 (en) | Double clutch type transmission | |
| CN105370820A (en) | Automatic ten-gear double-clutch transmission | |
| CN105370814A (en) | Multi-gear double-clutch transmission and vehicle | |
| CN204041899U (en) | Ten fast double-clutch automatic gearboxes | |
| CN105370815A (en) | Multi-gear double-clutch transmission and vehicle | |
| CN204025556U (en) | Ten fast double-clutch automatic gearboxes | |
| CN204025559U (en) | Ten fast double-clutch automatic gearboxes | |
| CN204025555U (en) | Ten fast double-clutch automatic gearboxes | |
| CN105202126A (en) | Seven-speed double-clutch type automatic transmission | |
| CN204004217U (en) | Eight speed double-clutch formula automatic transmission | |
| CN204025558U (en) | Ten fast double-clutch automatic gearboxes | |
| CN204025554U (en) | Ten fast double-clutch automatic gearboxes | |
| CN204041898U (en) | Ten fast double-clutch automatic gearboxes | |
| CN204025557U (en) | Ten fast double-clutch automatic gearboxes | |
| CN105370821A (en) | Ten-gear dual clutch automatic transmission | |
| CN204114024U (en) | Many gears double-clutch speed changer and vehicle | |
| CN203926631U (en) | Seven speed dual clutch formula automatic transmission | |
| CN204004218U (en) | Seven speed dual clutch formula automatic transmission | |
| CN203926635U (en) | Seven speed dual clutch formula automatic transmission | |
| CN201359059Y (en) | Multi-gear power shift planetary gearbox | |
| CN105370819A (en) | Automatic ten-gear double-clutch transmission | |
| CN105443678A (en) | Ten-speed dual clutch automatic transmission | |
| CN105443679A (en) | Ten-speed dual clutch automatic transmission | |
| CN105221674B (en) | Eight speed double-clutch formula automatic transmission | |
| CN105443682A (en) | Ten-speed dual clutch automatic transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20141217 Effective date of abandoning: 20180420 |
|
| AV01 | Patent right actively abandoned |