CN105443678B - Ten fast double-clutch automatic gearboxes - Google Patents
Ten fast double-clutch automatic gearboxes Download PDFInfo
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- CN105443678B CN105443678B CN201410436278.3A CN201410436278A CN105443678B CN 105443678 B CN105443678 B CN 105443678B CN 201410436278 A CN201410436278 A CN 201410436278A CN 105443678 B CN105443678 B CN 105443678B
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Abstract
The fast double-clutch automatic gearbox of one kind ten,Including 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,The automatic transmission uses the output axle construction of two groups of nested arrangements,The transmission of power is realized between two output shafts of wherein every group nested arrangement by a synchronizer,By way of borrowing gear,Realize ten forward gears and a reverse gear,The compact axial dimension of whole gearbox designs is small,Required installation space is smaller,Structure is relatively simple easy to process,With common seven,Eight speed transmissions can set ten gears on the premise of having identical overall dimensions,Gearratio distribution is more reasonable,Engine is set there are more probabilities to be operated in its best region,Improve dynamic property and economy.
Description
Technical field
The present invention relates to the transmission technology field of vehicle, more particularly to the fast double-clutch automatic gearbox of one kind ten.
Background technology
Double-clutch automatic gearbox (Dual Clutch Transmission, DCT) be by two gearboxes and two from
Clutch is integrated in a gearbox, and two input shafts being rotatably sleeved in together are connected with one of clutch respectively
Connect, two input shafts transmit the power of two gearbox speed groups respectively, by between two clutches automatically switch so as to
Gearshift program is completed, therefore can realize the power shift of gearshift procedure, i.e., interrupts power in gearshift procedure, overcomes automatically controlled
The shortcomings that automatic speed changer for machine (Automated Mechanical Transmission, AMT) shifting shock, vehicle is changing
During shelves, the power of engine all the time can be for delivery to wheel, and gear shift is steady rapidly, not only ensure that the acceleration of vehicle,
And since vehicle no longer produces the situation that is a significant slowdown caused by gear shift, also greatly improve the comfortable of vehicle operation
Property.
But existing double-clutch automatic gearbox is mostly to use double output shaft or single output shaft, therefore its axial ruler
It is very little longer, so for vehicle as preceding transverse engine, front-wheel drive, particularly compact car, due to its installation space by
To limitation, above-mentioned speed changer just more difficult use, and since the gear of its speed change is less, it is more difficult to realize gearratio rationally point
Match somebody with somebody, make engine is more difficult to be operated in optimum working zone, so as to have a negative impact to the dynamic property and economy of vehicle.
The content of the invention
In view of this, it is necessary to the fast double-clutch automatic gearbox of one kind ten is provided, its compact-sized axial dimension is small, by
In with ten forwards, make gearratio distribution more reasonable.
The embodiment of the present invention provides one kind ten fast double-clutch automatic gearbox, including：
The interior input shaft of mutually nested setting and outer input shaft, are installed on interior input shaft successively from close to engine one end
There are ten grades of driving gears, six grades of driving gears, fourth gear driving gear and a two grades of driving gears, from close to engine on outer input shaft
Rise and be sequentially installed with seven grades of driving gears, nine grades of driving gears and third speed drive gear in one end；
The first clutch being connected with interior input shaft；
The second clutch being connected with outer input shaft；
Output shaft and the first outer output shaft in the first of mutually nested setting, in first on output shaft and the first outer output shaft
The first final gear, nine grades of driven gears, the 6th synchronizer, third gear driven tooth are sequentially installed with from close to engine one end
Wheel, ten grades of driven gears, the 5th synchronizer, fourth gear driven gear and the 4th synchronizer；Wherein, the first final gear, nine grades
Driven gear and the 4th synchronizer are installed in first on output shaft, the 6th synchronizer, third gear driven gear, ten grades of driven tooths
Wheel, the 5th synchronizer and fourth gear driven gear are installed on the first outer output shaft；
Output shaft and the second outer output shaft in the second of mutually nested setting, in second on output shaft and the second outer output shaft
The second final gear, seven grades of driven gears, the first synchronizer, reverse gear driving tooth are sequentially installed with from close to engine one end
Wheel, the second synchronizer, six grades of driven gears, the 3rd synchronizer and two grades of driven gears；Wherein, the second final gear, seven grades
Driven gear and the first synchronizer are installed in second on output shaft, reverse driving gear, the second synchronizer, six grades of driven tooths
Wheel, the 3rd synchronizer and two grades of driven gears are installed on the second outer output shaft；
Wherein, two grades of driving gears are often engaged with two grades of driven gears, and third speed drive gear is often nibbled with third gear driven gear
Close, fourth gear driving gear is often engaged with fourth gear driven gear, and six grades of driving gears are often engaged with six grades of driven gears, seven grades of actives
Gear is often engaged with seven grades of driven gears, and nine grades of driving gears are often engaged with nine grades of driven gears, ten grades of driving gears and ten grades
Driven gear often engages, and reverse driving gear is often engaged with third gear driven gear；Each gear on interior input shaft and outer input shaft
It is each attached on corresponding axis or directly on corresponding axis and is formed, it is output shaft in first, the first outer output shaft, defeated in second
The equal empty set of each gear on shaft and the second outer output shaft in addition to the first final gear is with the second final gear is right
On the axis answered, the first final gear is fixed in first on output shaft, and the second final gear is fixed on output shaft in second
On, the tooth hub of each synchronizer is both connected on corresponding axis.
Further, the first synchronizer can be engaged with seven grades of driven gears and the second outer output shaft, and the second synchronizer can be with
Reverse driving gear and the engagement of six grades of driven gears, the 3rd synchronizer can be engaged with two grades of driven gears, and the 4th synchronizer can be with
First outer output shaft engagement, the 5th synchronizer can be engaged with fourth gear driven gear and ten grades of driven gears, and the 6th synchronizer can be with
Nine grades of driven gears and the engagement of third gear driven gear.
Further, the first synchronizer can be engaged with seven grades of driven gears and the second outer output shaft, and the second synchronizer can be with
Reverse driving gear engages, and the 3rd synchronizer can engage with six grades of driven gears and two grades of driven gears, and the 4th synchronizer can be with
First outer output shaft engagement, the 5th synchronizer can be engaged with fourth gear driven gear and ten grades of driven gears, and the 6th synchronizer can be with
Nine grades of driven gears and the engagement of third gear driven gear.
Further, the first outer output shaft is equipped with the first junction surface in one end away from engine, and the 4th synchronizer can be with
First junction surface engages.
Further, the second outer output shaft is equipped with the second junction surface in the one end for being close to engine, and the first synchronizer can be with
Second junction surface engages.
Further, which further includes differential mechanism gear ring, the first final gear and the second final gear
Often engaged with differential mechanism gear ring at the same time.
The fast double-clutch automatic gearbox of the ten of the present embodiment, by using the output axle construction of two groups of nested arrangements, wherein
The transmission of power is realized between two output shafts of every group of nested arrangement by a synchronizer, by way of borrowing gear,
Ten forward gears and a reverse gear are realized, the whole compact axial dimension of gearbox designs is small, required installation space is smaller, structure
It is relatively simple easy to process, ten shelves can be set on the premise of there are identical overall dimensions with common seven, eight speed transmissions
Position, gearratio distribution is more reasonable, makes engine have more probabilities to be operated in its best region, improves dynamic property and economy
Property.
Brief description of the drawings
Fig. 1 is the structure diagram of ten fast double-clutch automatic gearboxes of the embodiment of the present invention.
Embodiment
The present invention provides one kind ten fast double-clutch automatic gearbox, particularly a kind of to be suitable for preceding transverse engine, forerunner
Ten fast double-clutch automatic gearboxes of car, for existing double-clutch automatic gearbox axial length is big, required installation space
The problems such as larger, gearratio is not easy to distribute, gear number is few, there is provided a kind of axial length is small, required installation space is smaller, gearratio
Distribute the fast double-clutch automatic gearboxes of ten more compared with reasonable, gear number.To make the object, technical solutions and advantages of the present invention more
Add clear, embodiment of the present invention is further described below in conjunction with attached drawing.
Fig. 1 is the structure diagram of ten fast double-clutch automatic gearboxes of the embodiment of the present invention, please join Fig. 1, the present embodiment
Automatic transmission include：Output shaft 1,2, seven grades of driven gears 3 of the second final gear, the first synchronizer 4, reverse gear in second
Driving gear 5,6, six grades of driven gears 7 of the second synchronizer, 8, two grades of driven gears 9 of the 3rd synchronizer, the second outer output shaft 10,
Ten grades of 11, six grades of driving gear, 12, two grades of driving gear driving gears 13, interior input shaft 14, fourth gear driving gears the 15, the 4th are same
Walk 20, ten grades of output shaft 17, the first outer output shaft 18, fourth gear driven gear 19, the 5th synchronizer driven gears in device 16, first
21st, third gear driven gear 22, differential mechanism 23, differential mechanism gear ring 24, the 6th synchronizer 25,26, nine grades of the first final gear from
Moving gear 27, outer input shaft 28, engine 29, first clutch 30, second clutch 31, nine grades of driving gears 32, third gear masters
Moving gear 33 and seven grades of driving gears 34.
The automatic transmission includes six roots of sensation axis, is respectively：Output shaft 17, in interior input shaft 14, outer input shaft 28, first
1 and second outer output shaft 10 of output shaft, the six roots of sensation axis are horizontal positioned in one outer output shaft 18, second.
Interior input shaft 14 is hollow shaft with outer 28 mutually nested setting of input shaft, outer input shaft 28, and outer input shaft 28 is arranged
It is 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
Axis 14, second clutch 31 are connected with outer input shaft 28 and for controlling outer input shaft 28.
Output shaft 17 and the first outer 18 mutually nested setting of output shaft in first, the first outer output shaft 18 is hollow shaft, the
One outer output shaft 18 be set in first on output shaft 17 and with first in output shaft 17 it is coaxial.
Output shaft 1 and the second outer 10 mutually nested setting of output shaft in second, the second outer output shaft 10 are hollow shaft, second
Outer output shaft 10 be set in second on output shaft 1 and with second in output shaft 1 it is coaxial.Output shaft in interior input shaft 14, first
Output shaft 1 is arranged parallel in 17 and second.
On interior input shaft 14 ten grades of driving gears, 11, six grades of driving gears are sequentially installed with from close to engine one end
12nd, fourth gear driving gear 15 and two grades of driving gears 13.On outer input shaft 28 seven are sequentially installed with from close to engine one end
Shelves 34, nine grades of driving gears 32 of driving gear and third speed drive gear 33.
The first master is sequentially installed with first from close to engine one end on 17 and first outer output shaft 18 of output shaft to subtract
Fast 26, nine grades of driven gears 27 of gear, the 6th synchronizer 25, third gear driven gear 22, ten grades of driven gears 21, the 5th synchronizers
20th, 19 and the 4th synchronizer 16 of fourth gear driven gear.Wherein, 26, nine grades of driven gears 27 and the 4th of the first final gear are same
Walk device 16 to be installed in first on output shaft 17,22, ten grades of the 6th synchronizer 25, third gear driven gear driven gears the 21, the 5th
Synchronizer 20 and fourth gear driven gear 19 are installed on the first outer output shaft 18.
In second the second main deceleration is sequentially installed with from close to engine one end on 1 and second outer output shaft 10 of output shaft
6, six grades of 2, seven grades of driven gears 3 of gear, the first synchronizer 4, reverse driving gear 5, the second synchronizer driven gears the 7, the 3rd
Synchronizer 8 and two grades of driven gears 9.Wherein, 2, seven grades of 3 and first synchronizers 4 of driven gear of the second final gear are installed on
In second on output shaft 1, reverse driving gear 5,6, six grades of driven gears 7 of the second synchronizer, the 3rd synchronizer 8 and two grades are driven
Gear 9 is installed on the second outer output shaft 10.
Two grades of driving gears 13 are often engaged with two grades of driven gears 9, and third speed drive gear 33 and third gear driven gear 22 are normal
Engagement, fourth gear driving gear 15 are often engaged with fourth gear driven gear 19, and six grades of driving gears 12 are often nibbled with six grades of driven gears 7
Closing, seven grades of driving gears 34 are often engaged with seven grades of driven gears 3, and 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, and reverse driving gear 5 is often engaged with third gear driven gear 22；It is interior defeated
Enter each gear on axis 14 and outer input shaft 28 by welding, spline, interference be pressed etc. mode be fixed on corresponding axis or
Person is directly formed on corresponding axis, output shaft 17 in first, defeated outside output shaft 1 and second in the first outer output shaft 18, second
Each gear on shaft 10 in addition to the first final gear 26 is with the second final gear 2 is by bearing empty set corresponding
Axis on, the first final gear 26 is fixed in first on output shaft 17, and the second final gear 2 is fixed on output in second
On axis 1, the tooth hub of each synchronizer is connected on corresponding axis by spline.
Third speed drive gear 33 and reverse driving gear 5 are coplanar at the same time with third gear driven gear 22 often to engage
Gear set.First final gear 26 and the second final gear 2 are coplanar at the same time with differential mechanism gear ring 24 often to engage
Gear set.
First synchronizer 4 can be engaged with seven grades of 3 and second outer output shafts 10 of driven gear.In the present embodiment, second is same
Step device 6 can be engaged with reverse driving gear 5 and six grades of driven gears 7, and the 3rd synchronizer 8 can be engaged with two grades of driven gears 9, but
It is not limited, may be set to be in other embodiments：Second synchronizer 6 can be engaged with reverse driving gear 5, and the 3rd is same
Step device 8 can be engaged with six grades of driven gears 7 and two grades of driven gears 9.4th synchronizer 16 can be engaged with the first outer output shaft 18.
5th synchronizer 20 can be engaged with fourth gear driven gear 19 and ten grades of driven gears 21.6th synchronizer 25 can be with nine grades of driven tooths
Wheel 27 and third gear driven gear 22 engage.Specifically, the first outer output shaft 18 is equipped with the first engagement in one end away from engine
Portion 35, the 4th synchronizer 16 can be engaged with the first junction surface 35；Second outer output shaft 10 is equipped with the in the one end for being close to engine
Two junction surfaces 36, the first synchronizer 4 can be engaged with the second junction surface 36.Pass through the 4th synchronizer 16 and the first outer output shaft 18
Engagement, it is possible to achieve power is transmitted in the first outer output shaft 18 and first between output shaft 17；Pass through the first synchronizer 4
With the engagement of the second outer output shaft 10, it is possible to achieve power is passed in the second outer output shaft 10 and second between output shaft 1
Pass.
Each axis by bearings in case of transmission (not shown), gear and synchronizer on each axis perpendicular to
It is arranged in order on the direction of axis and is in substantially aligned setting, for example, two grades of driven gears, 9, two grades of driving gears 13 and the 4th is same
Step device 16 is in substantially aligned setting, and the 3rd synchronizer 8, fourth gear driving gear 15 and fourth gear driven gear 19 are set in substantially aligned
Put, six grades of driven gears, 7, six grades of 12 and the 5th synchronizers 20 of driving gear are in substantially aligned setting, remaining is similar, are so set
Structure can be made to become axial length that is more compact and effectively shortening speed changer.
Each shelves power transmission is as follows at work for the automatic transmission of the present embodiment：
One grade of power transmission route：6th synchronizer 25 and third gear driven gear 22 engage, the 5th synchronizer 20 and fourth gear
Driven gear 19 engages, and the 3rd synchronizer 8 and two grades of driven gears 9 engage, and the first synchronizer 4 and the second outer output shaft 10 connect
Close.Second clutch 31 closes, and engine torque passes to the third gear driving tooth on outer input shaft 28 by second clutch 31
Wheel 33, third gear driven gear 22 is passed to via third speed drive gear 33, by connecing for third gear driven gear 22 and the 6th synchronizer 25
Conjunction transfers torque to the 5th synchronizer 20, is transferred torque to by the engagement of the 5th synchronizer 20 and fourth gear driven gear 19 interior
On input shaft 14, then by two grades of driving gears 13 on interior input shaft 14 two grades of driven gears 9 are delivered to, by two grades of driven gears
9 and the 3rd the engagement of synchronizer 8 transfer torque to the second outer output shaft 10, then by the second outer 10 and first synchronizer of output shaft
4 engagement transfers torque to the second final gear 2 on output shaft 1 in second, then by differential mechanism gear ring 24, and finally
Power is exported by differential mechanism 23.
Two grades of power transmission routes：3rd synchronizer 8 and two grades of driven gears 9 engage, defeated outside the first synchronizer 4 and second
Shaft 10 engages.First clutch 30 closes, and engine torque passes to interior input shaft 14 by first clutch 30, via solid
Two grades of driving gears 13 being scheduled on interior input shaft 14 pass to two grades of driven gears 9, then synchronous with the 3rd by two grades of driven gears 9
The engagement of device 8 is transferred torque on the second outer output shaft 10, then will by the engagement of the second outer 10 and first synchronizer 4 of output shaft
Moment of torsion is delivered in second the second final gear 2 on output shaft 1, then by differential mechanism gear ring 24, and finally by differential mechanism
23 output power.
Third gear power transmission route：6th synchronizer 25 and third gear driven gear 22 engage, the 4th synchronizer 16 and first
Outer output shaft 18 engages.Second clutch 31 closes, and engine torque is passed on outer input shaft 28 by second clutch 31
Third speed drive gear 33, third gear driven gear 22 is passed to via third speed drive gear 33, by third gear driven gear 22 and the 6th
The engagement of synchronizer 25 is transferred torque on the first outer output shaft 18, then by the first outer 18 and the 4th synchronizer 16 of output shaft
Engagement transfers torque to the first final gear 26 in first on output shaft 17, then by differential mechanism gear ring 24, and finally
Power is exported by differential mechanism 23.
Fourth gear power transmission route：5th synchronizer 20 and fourth gear driven gear 19 engage, the 4th synchronizer 16 and first
Outer output shaft 18 engages.First clutch 30 closes, and engine torque passes to interior input shaft 14 by first clutch 30, warp
Fourth gear driven gear 19 is passed to by the fourth gear driving gear 15 being fixed on interior input shaft 14, then by fourth gear driven gear 19 and
The engagement of five synchronizers 20 is transferred torque on the first outer output shaft 18, then by the first outer 18 and the 4th synchronizer 16 of output shaft
Engagement transfer torque to the first final gear 26 in first on output shaft 17, then by differential mechanism gear ring 24, and most
Power is exported by differential mechanism 23 eventually.
Five grades of power transmission routes：6th synchronizer 25 and third gear driven gear 22 engage, the 5th synchronizer 20 and fourth gear
Driven gear 19 engages, 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 connect
Close.Second clutch 31 closes, and engine torque passes to the third gear driving tooth on outer input shaft 28 by second clutch 31
Wheel 33, passes to third gear driven gear 22, by connecing for 22 and the 6th synchronizer 25 of third gear driven gear via third speed drive gear 33
The 5th synchronizer 20 transferred torque on the first outer output shaft 18 is closed, then by the 5th synchronizer 20 and fourth gear driven gear 19
Engagement transfer torque to six grades of driving gears 12 on interior input shaft 14, six grades of driving gears 12 transfer torque to six grades
Driven gear 7, is transferred torque on the second outer output shaft 10 by the engagement of six grades of 7 and second synchronizers 6 of driven gear, then by
The engagement of second outer 10 and first synchronizer 4 of output shaft transfers torque to the second final gear in second on output shaft 1
2, then by differential mechanism gear ring 24, and power is finally exported by differential mechanism 23.
Six grades of power transmission routes：Second synchronizer 6 and six grades of driven gears 7 engage, defeated outside the first synchronizer 4 and second
Shaft 10 engages.First clutch 30 closes, and engine torque passes to interior input shaft 14 by first clutch 30, via solid
Six grades of driving gears 12 being scheduled on interior input shaft 14 pass to six grades of driven gears 7, then synchronous with second by six grades of driven gears 7
The engagement of device 6 is transferred torque on the second outer output shaft 10, then will by the engagement of the second outer 10 and first synchronizer 4 of output shaft
Moment of torsion is delivered in second the second final gear 2 on output shaft 1, then by differential mechanism gear ring 24, and finally by differential mechanism
23 output power.
Seven grades of power transmission routes：First synchronizer 4 and seven grades of driven gears 3 engage.Second clutch 31 closes, and starts
Machine moment of torsion passes to seven grades of driving gears 34 on outer input shaft 28 by second clutch 31, and seven grades of driving gears 34 are by moment of torsion
Seven grades of driven gears 3 are delivered to, output in second is transferred torque to by the engagement of seven grades of 3 and first synchronizers 4 of driven gear
The second final gear 2 on axis 1, then by differential mechanism gear ring 24, and power is finally exported by differential mechanism 23.
Eight grades of power transmission routes：5th synchronizer 20 and ten grades of driven gears 21 engage, the 6th synchronizer 25 and nine grades
Driven gear 27 engages, and the first synchronizer 4 and seven grades of driven gears 3 engage.First clutch 30 closes, and engine torque passes through
First clutch 30 passes to ten grades of driving gears 11 on interior input shaft 14, and ten grades of driving gears 11 transfer torque to ten grades
Driven gear 21, is transferred torque on the first outer output shaft 18 by the engagement of ten grades of 21 and the 5th synchronizers 20 of driven gear
6th synchronizer 25, then transferred torque to by the engagement of the 6th synchronizer 25 and nine grades of driven gears 27 on outer input shaft 28
Seven grades of driving gears 34, seven grades of driving gears 34 transfer torque to seven grades of driven gears 3, then by seven grades of driven gears 3 and
The engagement of one synchronizer 4 transfers torque to the second final gear 2 on output shaft 1 in second, then passes through differential mechanism gear ring
24, and power is finally exported by differential mechanism 23.
Nine grades of power transmission routes：6th synchronizer 25 and nine grades of driven gears 27 engage, the 4th synchronizer 16 and first
Outer output shaft 18 engages.Second clutch 31 closes, and engine torque is passed on outer input shaft 28 by second clutch 31
Nine grades of driving gears 32, nine grades of driving gears 32 transfer torque to nine grades of driven gears 27, by nine grades of 27 Hes of driven gear
The engagement of 6th synchronizer 25 is transferred torque on the first outer output shaft 18, then by the first outer 18 and the 4th synchronizer of output shaft
16 engagement transfers torque to the first final gear 26 on output shaft 17 in first, then by differential mechanism gear ring 24, and
Power is finally exported by differential mechanism 23.
Ten grades of power transmission routes：5th synchronizer 20 and ten grades of driven gears 21 engage, the 4th synchronizer 16 and first
Outer output shaft 18 engages.First clutch 30 closes, and engine torque passes to interior input shaft 14 by first clutch 30, warp
Ten grades of driven gears 21 are passed to by ten grades of driving gears 11 being fixed on interior input shaft 14, by ten grades of driven gears 21 and the 5th
The engagement of synchronizer 20 is transferred torque on the first outer output shaft 18, then by the first outer 18 and the 4th synchronizer 16 of output shaft
Engagement transfers torque to the first final gear 26 in first on output shaft 17, then by differential mechanism gear ring 24, and finally
Power is exported by differential mechanism 23.
Reverse gear power transmission route：3rd synchronizer 8 and two grades of driven gears 9 engage, and the second synchronizer 6 and reverse gear are actively
Gear 5 engages, 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, and engine torque passes to two grades of driving gears on interior input shaft 14 by first clutch 30
13, two grades of driving gears 13 transfer torque to two grades of driven gears 9, by the engagement of two grades of 9 and the 3rd synchronizers 8 of driven gear
The second synchronizer 6 on the second outer output shaft 10 is transferred torque to, since reverse driving gear 5 and third gear driven gear 22 are normal
Engagement, third gear driven gear 22 is transferred torque to by the engagement of the second synchronizer 6 and reverse driving gear 5, via third gear from
The engagement of 22 and the 6th synchronizer 25 of moving gear is transferred torque on the first outer output shaft 18, then by the first outer output shaft 18 with
The engagement of 4th synchronizer 16 transfers torque to the first final gear 26 on output shaft 17 in first, then passes through differential mechanism
Gear ring 24, and power is finally exported by differential mechanism 23.
The fast double-clutch automatic gearbox of the ten of the embodiment of the present invention, before being suitably applied on horizontal forerunner's car, it includes
Interior input shaft, the outer input shaft of setting nested with interior input shaft, output shaft in first, it is nested with output shaft in first set the
One outer output shaft, output shaft and the second outer output shaft of setting nested with output shaft in second, the automatic transmission are adopted in second
With the output axle construction of two groups of nested arrangements, realized wherein passing through a synchronizer between two output shafts of every group of nested arrangement
The transmission of power, by way of borrowing gear, realizes ten forward gears and a reverse gear, the whole compact axis of gearbox designs
To size is small, required installation space is smaller, structure is relatively simple easy to process, there is phase with common seven, eight speed transmissions
Ten gears can be set on the premise of with overall dimensions, and gearratio distribution is more reasonable, makes engine there are more probabilities to work
In its best region, dynamic property and economy are improved.
Herein, term " comprising ", "comprising" or any other variant thereof is intended to cover non-exclusive inclusion, are removed
Include those listed key elements, but also other elements that are not explicitly listed can be included.
Herein, the involved noun of locality such as forward and backward, upper and lower is to be located at parts in attached drawing in figure and zero
Part mutual position defines, only for the purpose of expressing the technical solution clearly and conveniently.It should be appreciated that the noun of locality
Use should not limit the claimed scope of the application.
In the case where there is no conflict, the feature in embodiment and embodiment herein-above set forth can be combined with each other.
The foregoing is merely presently preferred embodiments of the present invention, is not intended to limit the invention, it is all the present invention spirit and
Within principle, any modification, equivalent replacement, improvement and so on, should all be included in the protection scope of the present invention.
Claims (6)
1. the fast double-clutch automatic gearbox of one kind ten, it is characterised in that including：
The interior input shaft (14) of mutually nested setting and outer input shaft (28), from close to engine one end on interior input shaft (14)
It is sequentially installed with ten grades of driving gears (11), six grades of driving gears (12), fourth gear driving gear (15) and two grades of driving gears
(13), seven grades of driving gears (34), nine grades of driving gears are sequentially installed with from close to engine one end on outer input shaft (28)
(32) and third speed drive gear (33)；
The first clutch (30) being connected with interior input shaft (14)；
The second clutch (31) being connected with outer input shaft (28)；
Output shaft (17) and the first outer output shaft (18) in the first of mutually nested setting, in first outside output shaft (17) and first
On output shaft (18) from be sequentially installed with close to engine one end the first final gear (26), nine grades of driven gears (27),
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)；Wherein, the first final gear (26), nine grades of driven gears (27) and the 4th synchronizer (16)
On output shaft in first (17), the 6th synchronizer (25), third gear driven gear (22), ten grades of driven gears (21),
Five synchronizers (20) and fourth gear driven gear (19) are installed on the first outer output shaft (18)；
Output shaft (1) and the second outer output shaft (10) in the second of mutually nested setting, output shaft (1) and second defeated outside in second
On shaft (10) the second final gear (2), seven grades of driven gears (3), first are sequentially installed with from close to engine one end
Synchronizer (4), reverse driving gear (5), the second synchronizer (6), six grades of driven gears (7), the 3rd synchronizer (8) and two grades from
Moving gear (9)；Wherein, the second final gear (2), seven grades of driven gears (3) and the first synchronizer (4) are installed on defeated in second
On shaft (1), reverse driving gear (5), the second synchronizer (6), six grades of driven gears (7), the 3rd synchronizer (8) and two grades from
Moving gear (9) is installed on the second outer output shaft (10)；
Wherein, two grades of driving gears (13) are often engaged with two grades of driven gears (9), third speed drive gear (33) and third gear driven tooth
Take turns (22) often to engage, fourth gear driving gear (15) often engages with fourth gear driven gear (19), six grades of driving gears (12) and six grades
Driven gear (7) often engages, and seven grades of driving gears (34) often engage with seven grades of driven gears (3), nine grades of driving gears (32) and
Nine grades of driven gears (27) are often engaged, and ten grades of driving gears (11) are often engaged with ten grades of driven gears (21), reverse driving gear
(5) often engaged with third gear driven gear (22)；Each gear on interior input shaft (14) and outer input shaft (28) is each attached to correspondence
Axis on or directly formed on corresponding axis, output shaft (17) in first, the first outer output shaft (18), output shaft in second
(1) each gear and on the second outer output shaft (10) in addition to the first final gear (26) and the second final gear (2)
Equal empty set is on corresponding axis, and the first final gear (26) is fixed on output shaft in first (17), the second final gear
(2) it is fixed on output shaft in second (1), the tooth hub of each synchronizer is both connected on corresponding axis.
2. as claimed in claim 1 ten fast double-clutch automatic gearboxes, it is characterised in that：First synchronizer (4) can be with seven grades
Driven gear (3) and the second outer output shaft (10) engagement, the second synchronizer (6) can be driven with reverse driving gear (5) and six grades
Gear (7) engages, and the 3rd synchronizer (8) can be engaged with two grades of driven gears (9), and the 4th synchronizer (16) can be with exporting outside first
Axis (18) engages, and the 5th synchronizer (20) can be engaged with fourth gear driven gear (19) and ten grades of driven gears (21), and the 6th is synchronous
Device (25) can be engaged with nine grades of driven gears (27) and third gear driven gear (22).
3. as claimed in claim 1 ten fast double-clutch automatic gearboxes, it is characterised in that：First synchronizer (4) can be with seven grades
Driven gear (3) and the second outer output shaft (10) engagement, the second synchronizer (6) can be engaged with reverse driving gear (5), and the 3rd is same
Step device (8) can be engaged with six grades of driven gears (7) and two grades of driven gears (9), and the 4th synchronizer (16) can be with exporting outside first
Axis (18) engages, and the 5th synchronizer (20) can be engaged with fourth gear driven gear (19) and ten grades of driven gears (21), and the 6th is synchronous
Device (25) can be engaged with nine grades of driven gears (27) and third gear driven gear (22).
4. as claimed in claim 1 ten fast double-clutch automatic gearboxes, it is characterised in that：First outer output shaft (18) is in remote
One end of engine is equipped with the first junction surface (35), and the 4th synchronizer (16) can be engaged with the first junction surface (35).
5. as claimed in claim 1 ten fast double-clutch automatic gearboxes, it is characterised in that：Second outer output shaft (10) is in being close to
One end of engine is equipped with the second junction surface (36), and the first synchronizer (4) can be engaged with the second junction surface (36).
6. as claimed in claim 1 ten fast double-clutch automatic gearboxes, it is characterised in that：The automatic transmission further includes differential
Device gear ring (24), the first final gear (26) and the second final gear (2) while often engaged with differential mechanism gear ring (24).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410436278.3A CN105443678B (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410436278.3A CN105443678B (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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| Publication Number | Publication Date |
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| CN105443678A CN105443678A (en) | 2016-03-30 |
| CN105443678B true CN105443678B (en) | 2018-05-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410436278.3A Active CN105443678B (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| 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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|---|---|---|---|---|
| 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 |
| CN202468867U (en) * | 2011-12-26 | 2012-10-03 | 叶文森 | Parallel planetary gear transmission twin-countershaft transmission drive axle |
| 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 |
| 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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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7597644B2 (en) * | 2007-05-21 | 2009-10-06 | Gm Global Technology Operations, Inc. | Nine or ten speed split clutch countershaft automatic transmission |
| FR2971572B1 (en) * | 2011-02-10 | 2014-03-14 | Pascal Thery | DOUBLE CLUTCH GEARBOX COMPRISING A TRANSFER LINK |
| JP5330470B2 (en) * | 2011-08-31 | 2013-10-30 | 本田技研工業株式会社 | Transmission control device |
| 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 |
| 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 |
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- 2014-08-29 CN CN201410436278.3A patent/CN105443678B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN202468867U (en) * | 2011-12-26 | 2012-10-03 | 叶文森 | Parallel planetary gear transmission twin-countershaft transmission drive axle |
| 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 |
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| CN105443678A (en) | 2016-03-30 |
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