CN105443682B - Ten fast double-clutch automatic gearboxes - Google Patents
Ten fast double-clutch automatic gearboxes Download PDFInfo
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- CN105443682B CN105443682B CN201410438891.9A CN201410438891A CN105443682B CN 105443682 B CN105443682 B CN 105443682B CN 201410438891 A CN201410438891 A CN 201410438891A CN 105443682 B CN105443682 B CN 105443682B
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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 transmitting of power is wherein realized between two output shafts of every group of nested arrangement by a synchronizer,By way of borrowing gear,Realize ten forward gears and a reverse gear,The compact axial dimension of entire gearbox designs is small,Required installation space is smaller,Structure is relatively simple easy to process,With common seven,Eight speed transmissions have settable ten gears under the premise of identical overall dimensions,Transmission ratio distribution is more reasonable,Engine is set there are more probability work in its best region,Improve dynamic property and economy.
Description
Technical field
The present invention relates to the transmission technology fields of vehicle, more particularly to the fast double-clutch automatic gearbox of one kind ten.
Background technique
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 to
Shift 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 always 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 generates the situation that is a significant slowdown due to caused by gear shift, the comfortable of vehicle operation is also greatly improved
Property.
But existing double-clutch automatic gearbox mostly uses 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, especially 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 transmission ratio rationally point
Match, makes the more difficult work of engine in optimum working zone, so that the dynamic property and economy to vehicle have an adverse effect.
Summary of the invention
In view of this, compact-sized axial dimension is small it is necessary to provide the fast double-clutch automatic gearbox of one kind ten, by
In having ten forwards, keep transmission ratio 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 successively installed from close to engine one end on interior input shaft
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
It rises and is sequentially installed with seven or 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 mounted 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 mounted 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, third synchronizer and two grades of driven gears；Wherein, the second final gear, seven grades
Driven gear and the first synchronizer are mounted in second on output shaft, reverse driving gear, the second synchronizer, six grades of driven tooths
Wheel, third synchronizer and two grades of driven gears are mounted 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
It closes, 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 or nine grades of masters
Moving gear is often engaged with nine grades of driven gears and seven grades of driven gears simultaneously, and ten grades of driving gears are often nibbled with ten grades of driven gears
It closes, reverse driving gear is often engaged with third gear driven gear；Each gear on interior input shaft and outer input shaft is each attached to correspondence
Axis on or directly formed on corresponding axis, output shaft in first, the first outer output shaft, in second outside output shaft and second
The equal empty set of each gear on output shaft in addition to the first final gear other than the second final gear is on corresponding axis, and first
Final gear is fixed in first on output shaft, and the second final gear is fixed in second on output shaft, each synchronizer
Tooth hub 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, third 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 engagement, third 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 joint portion in one end far from engine, and the 4th synchronizer can be with
The engagement of first joint portion.
Further, the second outer output shaft is equipped with the second joint portion in the one end for being close to engine, and the first synchronizer can be with
The engagement of second joint portion.
Further, which further includes differential mechanism gear ring, the first final gear and the second final gear
It is often engaged with differential mechanism gear ring simultaneously.
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 transmitting for realizing power 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 entire compact axial dimension of gearbox designs is small, required installation space is smaller, structure
It is relatively simple easy to process, settable ten shelves under the premise of there are identical overall dimensions with common seven, eight speed transmissions
Position, transmission ratio distribution is more reasonable, makes engine have more probability work in its best region, improves dynamic property and economy
Property.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of ten fast double-clutch automatic gearboxes of the embodiment of the present invention.
Specific embodiment
The present invention provides one kind ten fast double-clutch automatic gearbox, especially a kind of to be suitable for preceding transverse engine, forerunner
The fast double-clutch automatic gearboxes of the ten of car, for existing double-clutch automatic gearbox axial length is big, required installation space
The problems such as larger, transmission ratio is not easy to distribute, gear number is few, provides that a kind of axial length is small, required installation space is smaller, transmission ratio
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 structural schematic 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, third synchronizer 8, two grades of driven gears 9, 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 gear 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
21, 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 31,79 grades of driving gears 32 and third gear
Driving gear 33.
The automatic transmission includes six roots of sensation axis, respectively：Output shaft 17, in interior input shaft 14, outer input shaft 28, first
Output shaft 1 and the second outer output shaft 10 in one outer output shaft 18, second, the six roots of sensation axis are horizontal positioned.
The setting mutually nested with outer input shaft 28 of interior input shaft 14, outer input shaft 28 are hollow shaft, 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.
The setting mutually nested with the first outer output shaft 18 of output shaft 17 in first, the first outer output shaft 18 are 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.
The setting mutually nested with the second outer output shaft 10 of output shaft 1 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.
Ten grades of driving gears, 11, six grades of driving gears are sequentially installed with from close to engine one end on interior input shaft 14
12, fourth gear driving gear 15 and two grades of driving gears 13.Seven are sequentially installed with from close to engine one end on outer input shaft 28
Nine grades of driving gears 32 and third speed drive gear 33.
The first master is sequentially installed in first on output shaft 17 and the first outer output shaft 18 from close to engine one end to subtract
26, nine grades of driven gears 27 of fast gear, the 6th synchronizer 25, third gear driven gear 22, ten grades of driven gears 21, the 5th synchronizers
20, fourth gear driven gear 19 and the 4th synchronizer 16.Wherein, 26, nine grades of driven gears 27 of the first final gear and the 4th same
Step device 16 is mounted 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 mounted on the first outer output shaft 18.
The second main deceleration is sequentially installed with from close to engine one end on output shaft 1 and the second outer output shaft 10 in second
2, seven grades of driven gears 3 of gear, the first synchronizer 4, reverse driving gear 5, the second synchronizer 6, six grades of driven gears 7, third
Synchronizer 8 and two grades of driven gears 9.Wherein, 2, seven grades of driven gears 3 of the second final gear and the first synchronizer 4 are mounted on
In second on output shaft 1, reverse driving gear 5,6, six grades of driven gears 7 of the second synchronizer, third synchronizer 8 and two grades are driven
Gear 9 is mounted 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
Close, seven or nine grades of driving gears 32 are often engaged with nine grades of driven gears 27 and seven grades of driven gears 3 simultaneously, ten grades of driving gears 11 and
Ten grades of driven gears 21 often engage, and reverse driving gear 5 is often engaged with third gear driven gear 22；Interior input shaft 14 and outer input shaft
Each gear on 28 is fixed on corresponding axis or by modes such as welding, spline, interference press fittings directly in corresponding axis
Upper formation, output shaft 17 in first, in the first outer output shaft 18, second on output shaft 1 and the second outer output shaft 10 in addition to first
Final gear 26 passes through bearing empty set on corresponding axis with each gear except the second final gear 2, and the first master subtracts
Fast gear 26 is fixed in first on output shaft 17, and the second final gear 2 is fixed in second on output shaft 1, each synchronizer
Tooth hub pass through spline and be connected on corresponding axis.
Third speed drive gear 33 and reverse driving gear 5 are coplanar simultaneously with third gear driven gear 22 often to engage
Gear set.Nine grades of driven gears 27 and seven grades of driven gears 3 are coplanar simultaneously with seven or nine grades of driving gears 32 often to engage
Gear set.First final gear 26 and the second final gear 2 are coplanar simultaneously with differential mechanism gear ring 24 often to engage
Gear set.
First synchronizer 4 can be engaged with seven grades of driven gears 3 and the second outer output shaft 10.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 third 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 third 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 far from engine
Portion 35, the 4th synchronizer 16 can be engaged with the first joint portion 35；Second outer output shaft 10 is equipped with the in the one end for being close to engine
Two joint portions 36, the first synchronizer 4 can be engaged with the second joint portion 36.Pass through the 4th synchronizer 16 and the first outer output shaft 18
Engagement, may be implemented power and is being transmitted between output shaft 17 in the first outer output shaft 18 and first；Pass through the first synchronizer 4
With the engagement of the second outer output shaft 10, power may be implemented and passed between output shaft 1 in the second outer output shaft 10 and second
It passs.
Each axis passes through bearing support in case of transmission (not shown), the gear and synchronizer on each axis perpendicular to
It is arranged successively 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 are together
Walking device 16 is in substantially aligned setting, and third synchronizer 8, fourth gear driving gear 15 and fourth gear driven gear 19 are set in substantially aligned
It sets, six grades of driven gears, 7, six grades of driving gears 12 and the 5th synchronizer 20 are in substantially aligned setting, remaining is similar, are arranged in this way
Structure can be made to become more compact and effectively shorten the axial length of 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 third synchronizer 8 and two grades of driven gears 9 engage, and the first synchronizer 4 and the second outer output shaft 10 connect
It closes.Second clutch 31 is closed, 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 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 transmitted to, by two grades of driven gears
9 transfer torque to the second outer output shaft 10 with the engagement of third synchronizer 8, then by the second outer output shaft 10 and the first synchronizer
4 engagement transfers torque to the second final gear 2 in second on output shaft 1, then by differential mechanism gear ring 24, and finally
By 23 output power of differential mechanism.
Two grades of power transmission routes：Third synchronizer 8 and two grades of driven gears 9 engage, defeated outside the first synchronizer 4 and second
Shaft 10 engages.First clutch 30 is closed, 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 third by two grades of driven gears 9
The engagement of device 8 transfers torque on the second outer output shaft 10, then will by the engagement of the second outer output shaft 10 and the first synchronizer 4
Torque is transmitted 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 powers.
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 is closed, 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 transfers torque on the first outer output shaft 18, then by the first outer output shaft 18 and the 4th synchronizer 16
Engagement transfers torque to the first final gear 26 in first on output shaft 17, then by differential mechanism gear ring 24, and finally
By 23 output power of differential mechanism.
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 is closed, and engine torque passes to interior input shaft 14 by first clutch 30, is passed through
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 transfers torque on the first outer output shaft 18, then by the first outer output shaft 18 and the 4th synchronizer 16
Engagement transfer torque to the first final gear 26 in first on output shaft 17, then by differential mechanism gear ring 24, and most
Eventually by 23 output power of differential mechanism.
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
It closes.Second clutch 31 is closed, 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 via third speed drive gear 33, by connecing for third gear driven gear 22 and the 6th synchronizer 25
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 driven gears 7 and the second synchronizer 6, then by
The engagement of second outer output shaft 10 and the first synchronizer 4 transfers torque to the second final gear in second on output shaft 1
2, then by differential mechanism gear ring 24, and finally by 23 output power of differential mechanism.
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 is closed, 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 transfers torque on the second outer output shaft 10, then will by the engagement of the second outer output shaft 10 and the first synchronizer 4
Torque is transmitted 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 powers.
Seven grades of power transmission routes：First synchronizer 4 and seven grades of driven gears 3 engage.Second clutch 31 is closed, and is started
Machine torque passes to seven or nine grades of driving gears on outer input shaft 28,32,79 grades of driving gears 32 by second clutch 31 will
Torque is transmitted to seven grades of driven gears 3, is transferred torque in second by the engagement of seven grades of driven gears 3 and the first synchronizer 4
The second final gear 2 on output shaft 1, then by differential mechanism gear ring 24, and finally by 23 output power of differential mechanism.
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 is closed, 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 driven gears 21 and the 5th synchronizer 20
6th synchronizer 25, then transferred torque on outer input shaft 28 by the engagement of the 6th synchronizer 25 and nine grades of driven gears 27
Seven or nine grades of driving gears, 32,79 grades of driving gears 32 transfer torque to seven grades of driven gears 3, then by seven grades of driven gears 3
Engagement with the first synchronizer 4 transfers torque to the second final gear 2 in second on output shaft 1, then passes through differential mechanism
Gear ring 24, and finally by 23 output power of differential mechanism.
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 is closed, and engine torque is passed on outer input shaft 28 by second clutch 31
Seven or nine grades of driving gears, 32,79 grades of driving gears 32 transfer torque to nine grades of driven gears 27, by nine grades of driven gears
27 and the 6th the engagement of synchronizer 25 transfer torque on the first outer output shaft 18, then it is same by the first outer output shaft 18 and the 4th
The engagement of step device 16 transfers torque to the first final gear 26 in first on output shaft 17, then passes through differential mechanism gear ring
24, and finally by 23 output power of differential mechanism.
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 is closed, and engine torque passes to interior input shaft 14 by first clutch 30, is passed through
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 transfers torque on the first outer output shaft 18, then by the first outer output shaft 18 and the 4th synchronizer 16
Engagement transfers torque to the first final gear 26 in first on output shaft 17, then by differential mechanism gear ring 24, and finally
By 23 output power of differential mechanism.
Reverse gear power transmission route：Third 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 is closed, 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 driven gears 9 and third synchronizer 8
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 transfers torque to third gear driven gear 22 by the engagement of the second synchronizer 6 and reverse driving gear 5, via third gear from
The engagement of moving gear 22 and the 6th synchronizer 25 transfers 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 in first on output shaft 17, then passes through differential mechanism
Gear ring 24, and finally by 23 output power of differential mechanism.
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 comprising
Interior input shaft, the outer input shaft of setting nested with interior input shaft, output shaft in first, setting nested with output shaft in first 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 transmitting of power realizes ten forward gears and a reverse gear, the entire compact axis of gearbox designs by way of borrowing gear
Small to size, required installation space is smaller, structure is relatively simple easy to process, has phase with common seven, eight speed transmissions
Settable ten gears under the premise of with overall dimensions, transmission ratio distribution is more reasonable, and engine is made to have more probabilities to work
In its best region, dynamic property and economy are improved.
Herein, the terms "include", "comprise" or any other variant thereof is intended to cover non-exclusive inclusion, are removed
It comprising those of listed element, but also may include other elements that are not explicitly listed.
Herein, the nouns of locality such as related front, rear, top, and bottom are to be located in figure with components in attached drawing 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 range of the application.
In the absence of 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 in spirit of the invention and
Within principle, any modification, equivalent replacement, improvement and so on be 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, which is characterized 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 or nine grades of driving gears (32) and third gear driving tooth are sequentially installed with from close to engine one end on outer input shaft (28)
It takes turns (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)
It is mounted 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 mounted 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
The second final gear (2), seven grades of driven gears (3), first are sequentially installed with from close to engine one end on shaft (10)
Synchronizer (4), reverse driving gear (5), the second synchronizer (6), six grades of driven gears (7), third 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 mounted on defeated in second
On shaft (1), reverse driving gear (5), the second synchronizer (6), six grades of driven gears (7), third synchronizer (8) and two grades from
Moving gear (9) is mounted 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
It takes 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 or nine grades of driving gears (32) are normal with nine grades of driven gears (27) and seven grades of driven gears (3) simultaneously
Engagement, ten grades of driving gears (11) are often engaged with ten grades of driven gears (21), reverse driving gear (5) and third gear driven gear
(22) often engagement；Each gear on interior input shaft (14) and outer input shaft (28) is each attached on corresponding axis or directly right
It is formed on the axis answered, output shaft (17) in first, the first outer output shaft (18), output shaft (1) and the second outer output shaft in second
(10) the equal empty set of each gear in addition to the first final gear (26) other than the second final gear (2) is in corresponding axis
On, the first final gear (26) is fixed on output shaft in first (17), and the second final gear (2) is fixed on defeated in second
On shaft (1), the tooth hub of each synchronizer is both connected on corresponding axis.
2. as described 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) engagement, third synchronizer (8) can be engaged with two grades of driven gears (9), and the 4th synchronizer (16) can export outside with first
Axis (18) engagement, 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 described 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 third 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 export outside with first
Axis (18) engagement, 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 described in claim 1 ten fast double-clutch automatic gearboxes, it is characterised in that：First outer output shaft (18) is in separate
One end of engine is equipped with the first joint portion (35), and the 4th synchronizer (16) can be engaged with the first joint portion (35).
5. as described 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 joint portion (36), and the first synchronizer (4) can be engaged with the second joint portion (36).
6. as described 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) are often engaged with differential mechanism gear ring (24) simultaneously.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410438891.9A CN105443682B (en) | 2014-08-29 | 2014-08-29 | Ten fast double-clutch automatic gearboxes |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410438891.9A CN105443682B (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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| CN105443682A CN105443682A (en) | 2016-03-30 |
| CN105443682B true CN105443682B (en) | 2018-11-23 |
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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 |
| 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 |
| CN204025556U (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 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5330470B2 (en) * | 2011-08-31 | 2013-10-30 | 本田技研工業株式会社 | Transmission control device |
-
2014
- 2014-08-29 CN CN201410438891.9A patent/CN105443682B/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 |
| CN204025556U (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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105443682A (en) | 2016-03-30 |
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