CN107917167A - Eight fast double-clutch automatic gearboxes - Google Patents
Eight fast double-clutch automatic gearboxes Download PDFInfo
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- CN107917167A CN107917167A CN201610878119.8A CN201610878119A CN107917167A CN 107917167 A CN107917167 A CN 107917167A CN 201610878119 A CN201610878119 A CN 201610878119A CN 107917167 A CN107917167 A CN 107917167A
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- driving
- output shaft
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- 210000000515 tooth Anatomy 0.000 claims description 21
- 238000003825 pressing Methods 0.000 claims description 12
- 230000005540 biological transmission Effects 0.000 claims description 11
- 238000000926 separation method Methods 0.000 claims description 10
- 239000004744 fabric Substances 0.000 claims description 4
- 230000004323 axial length Effects 0.000 abstract description 3
- 230000008450 motivation Effects 0.000 description 6
- 230000008901 benefit Effects 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 230000017105 transposition Effects 0.000 description 1
Classifications
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- 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
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- 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
- F16H3/085—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 with more than one output shaft
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- 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
- F16H3/12—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 with means for synchronisation not incorporated in the clutches
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- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
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- 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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
Abstract
The invention discloses the fast double-clutch automatic gearbox of one kind eight, including double clutch, first, second input shaft, first, second output shaft and differential mechanism, first, second input shaft coaxial package arrangement；Be fixed with first input shaft one reverse gear, five or seven gears, three gear driving gears；Six gears, four gears, two gear driving gear are fixed with second input shaft；A gear, five gears, six gears, two gear driven gears are set with first output shaft, be set with the second output shaft reverse gear, seven gears, three gears, four gear driven gears；First output shaft be equipped with one gear, five gear, two gear, six gear synchronizers, the second output shaft be equipped with reverse gear, seven gear, three gear, four gear synchronizers, and eight gear synchronizers be fixed on five gear driven gears；First, second output shaft is connected by first, second main deceleration driving gear and final gear with differential mechanism.The present invention is effectively shortened the axial length and radical length of speed changer, simplifies structure.
Description
Technical field
The present invention relates to vehicle drive system field, more particularly to it is a kind of be applied to using internal combustion engine as the vehicle of power eight
Fast double-clutch automatic gearbox.
Background technology
It is faced with evolution as the automobile of power using internal combustion engine and is constantly carried under the premise of dynamic property, comfort is ensured
Efficient challenge.Compared with traditional fluid torque-converter, planetary gear type automatic transmission, double-clutch automatic gearbox efficiency
Higher, shift time is shorter, there is obvious advantage.It is, in general, that the double-clutch automatic gearbox of more gear can increase
Gear range, is conducive to improve wheel torque during starting, engine working speed is reduced, so that improve power assembly is
Efficiency of uniting and power performance.However, with the increase of gear quantity, the size of speed changer can inevitably increase.It is especially right
For preposition forerunner's vehicle, the increase of transmission dimensions can bring difficulty to arrangement.
Therefore, reducing the size of double-clutch automatic gearbox as far as possible becomes the main mesh of many existing invention or utility model
Mark.It is with disclosed " a kind of double-clutch automatic gearbox for vehicle " (CN201310442936) in Chinese patent literature
, only 4 gears in its input axis so that axial length is short.But since shared driving gear is excessive, and actively
Gear is the gear that intensity is weaker in gear pair again, therefore, adds the difficulty of design of gears, reduces the reliable of speed changer
Property.
The content of the invention
In order to solve the drawbacks described above in existing double-clutch speed changer technology, the present invention propose a kind of axial dimension it is short,
Eight small, simple and compact for structure fast double-clutch automatic gearboxes of radial dimension.
The technical proposal of the invention is realized in this way：
The fast double-clutch automatic gearbox of one kind eight, including double clutch, the first input shaft, the second input shaft, the first output
Axis, the second output shaft and differential mechanism,
The double clutch includes the first automatic clutch and the second automatic clutch, two input shafts and two output shafts
Between be mutually arranged in parallel, first input shaft is connected with first automatic clutch, second input shaft with
Second automatic clutch is connected, and first input shaft is arranged with second input shaft with coaxial package, and described
Including one input shaft, outside, first input shaft stretches out described the to second input shaft in one end away from double clutch
Two input shafts；
Be fixed with first input shaft one reverse gear driving gear, five or seven gear driving gears, three gear driving gears, one gear
Shared one reverse gear driving gear with reversing gear, five gears share five or seven gear driving gears with seven gears；It is fixed with second input shaft
Six gear driving gears, four gear driving gears, two gear driving gear；Correspondingly, to be set with a gear on first output shaft driven
Any two in gear, five gear driven gears and six gear driven gears, two gear driven gears, four gear driven gears, it is described
The driven gear that reverses gear, seven gear driven gears, three gear driven gears and six gear driven gears, two gears are set with second output shaft
One on the first output shaft is not arranged in driven gear, four gear driven gears；It is synchronous that first output shaft is equipped with a gear
Any two in device, five gear synchronizers and six gear synchronizers, two gear synchronizers, four gear synchronizers, second output shaft
It is equipped with reverse gear synchronizer, seven gear synchronizers, three gear synchronizers, six gear synchronizers, two gear synchronizers and four gear synchronizers not
One on the first output shaft, and eight gear synchronizers are equipped with five gear driven gears, the eight gears synchronizer is with being arranged on
Six gear driven gears or four gear driven gears or two gear driven gear engagements and separation on first output shaft；Described first
Output shaft is fixed with the first main deceleration driving gear close to one end of double clutch, and second output shaft is close to double clutch
One end is fixed with the second main deceleration driving gear, and the first main deceleration driving gear, the second main deceleration driving gear are same
Shi Yuyi final gears engage, which is fixed on the differential mechanism.
Further, described one driving gear that reverses gear is arranged on first input shaft apart from double clutch distalmost end,
On first output shaft corresponding suit with this one reverse gear that driving gear is meshed described one keep off driven gear, and be disposed with phase
One answered keeps off synchronizer, and the driven tooth of reversing gear being meshed with described one gear driven gear is accordingly set with second output shaft
Wheel, and it is disposed with corresponding reverse gear synchronizer.
Further, it is described five or seven gear driving gear be arranged in one reverse gear driving gear with six gear driving gears or four keep off from
Between moving gear or two gear driven gears, five to be meshed with described 57 gear driving gears are set with first output shaft
Gear driven gear is simultaneously disposed with corresponding five gears synchronizer, is set with second output shaft and described 57 gear driving gears
Seven to be meshed keep off driven gears and are disposed with corresponding seven gears synchronizer；It is driven that the eight gears synchronizer is fixed on five gear
Engage and separate on gear and with described six gear driven gears or four gear driven gears or two gear driven gears.
Further, first automatic clutch includes the first driving disc spacing pressing and the first clutch plate, first driving disc spacing pressing
With the connection of spline slide and moment of torsion is transmitted between the shell of double clutch, first clutch plate and first input shaft
Between be splined transmission moment of torsion；Second automatic clutch includes the second driving disc spacing pressing and the second clutch plate, and described second
With the connection of spline slide and moment of torsion is transmitted between driving disc spacing pressing and the shell of double clutch, second clutch plate and described second
Transmission moment of torsion is splined between input shaft.
Further, parking ratchet wheel is further included, the parking ratchet wheel is arranged on first output shaft or described second
On output shaft or on the differential mechanism.
The beneficial effects of the invention are as follows：The present invention provides one kind eight fast double-clutch automatic gearbox, does not use usually eight
Eight widely used gear driving gears, eight gear driven gear structures in fast double-clutch automatic gearbox, but pass through six gears, five
Gear, the gears of seven gears and synchronizer realize eight gears, are thus effectively shortened the axial length of speed changer, and simplification finishes
Structure.And the present invention does not use widely used reverse gear shaft usually in eight fast double-clutch automatic gearboxes, but reverse gear using one
As soon as driving gear, gear driven gear, reverse gear driven gear and reverse gear synchronizer reverses gear to realize, in this way, effectively shortening
The radical length of speed changer, further simplify structure.Technique effect with the following aspects：
First, it can realize 8 forward gears and 1 reverses gear.Wherein, a gear gearratio is a gear driven gear number of teeth and one
Reverse gear the ratio between driving gear number of teeth, two gear gearratios are two gear the ratio between the driven gear numbers of teeth and the two gear driving gear number of teeth, and three keep off
Gearratio is the three gear driven gear numbers of teeth and three gear the ratio between driving gear numbers of teeth, four gear gearratios for the four gear driven gear numbers of teeth with
The ratio between four gear driving gear numbers of teeth, five keep off gearratios as the ratio between the five gear driven gear numbers of teeth and five or the seven gear driving gear numbers of teeth, and six
Keep off gearratio and keep off the ratio between driving gear numbers of teeth for the six gear driven gear numbers of teeth and six, seven gear gearratios are the seven gear driven gear numbers of teeth
The ratio between driving gear numbers of teeth are kept off with five or seven, eight gear gearratios keep off gearratios divided by five for six gear gearratios or four gear gearratios or two
Gearratio is kept off multiplied by with seven gear gearratios, (i.e. one reverses gear the driven gear number of teeth back gear ratio with the driving gear that reverses gear to reverse gear
The ratio between driving gear) number of teeth；
Second, axial dimension is short.It is axial only to arrange 7 gear pairs and 3 synchronizers；
3rd, radial dimension is small.Reverse gear shaft is eliminated, only 4 axis, reduce radial dimension to greatest extent；
4th, shafting deformation is small, and noise and vibration is small.One gear, two gears and reversing gear are arranged in shafting both ends close at bearing,
Stress is best；
5th, differential mechanism and a gear driven gear interference possibility are small.Differential mechanism and a gear driven gear are arranged in
The both ends of shafting, avoid because a gear speed than it is excessive or caused by differential mechanism is excessive it is dry between a gear driven gear and differential mechanism
Relate to；
6th, Speed Ratio Distribution and design of gears are convenient.Only 5/7 gear is high gear to share driving gear, is conducive to speed
Score is matched somebody with somebody and design of gears；
7th, scalability is good.By the optimization and the analysis of number of gear teeth to coordinating between synchronizer, in existing structure
It is lower to there is a possibility that to increase gear.
Brief description of the drawings
Fig. 1 is fast 1 schematic diagram of double-clutch automatic gearbox embodiment of the present invention eight；
Fig. 2 is fast 2 schematic diagram of double-clutch automatic gearbox embodiment of the present invention eight；
With reference to attached drawing, make the following instructions：
The first input shafts of 1-, the second input shafts of 2-, the first output shafts of 3-, the second output shafts of 4-, 11- mono- reverse gear driving tooth
Wheel, 31- mono- keep off driven gear, 22- two gear driving gears, 32- bis- keep off driven gear, 13- tri- keep off driving gear, 43- tri- keep off from
Moving gear, 24- tetra- keep off driving gear, and 44- tetra- keeps off driven gear, and 15- five or seven keeps off driving gear, and 35- five keeps off driven gear, 26-
Six gear driving gears, 36- six keep off driven gear, and 47- seven keeps off driven gear, and 49- reverses gear driven gear, and S1- mono- keeps off synchronizer,
S2- bis- keeps off synchronizer, and S3- tri- keeps off synchronizer, and S4- tetra- keeps off synchronizer, and S5- five keeps off synchronizer, and S6- six keeps off synchronizer, and S7- seven is kept off
Synchronizer, S8- eight keep off synchronizer, SR- reverse gear synchronizers, the first main deceleration driving gears of 30-, the main deceleration driving tooths of 40- second
Wheel, 50- final gears, 100- double clutches, the first automatic clutches of C1-, the second automatic clutches of C2-, 600- parking spine
Wheel.
Embodiment
In order to be more clearly understood that the technology contents of the present invention, described in detail especially exemplified by following embodiments, its purpose is only
It is to be best understood from the protection domain that present disclosure is not intended to limit the present invention.
Embodiment 1
As shown in Figure 1, the eight fast double-clutch automatic gearboxes applied to automobile include first two on the same axis
Automatic clutch C1 and the second automatic clutch C2, the first input shaft 1, the second input shaft 2, the first output shaft 3, the second output shaft
4th, the first main deceleration driving gear 30, the second main deceleration driving gear 40, final gear 50, differential mechanism 5.The bent axle of engine
It is connected by flexible disc with the shell of double clutch.Mutually parallel cloth between two input shafts 1,2 and two output shafts 3,4
Put.Double clutch 100, which includes the first automatic clutch C1 and the second automatic clutch C2, the first automatic clutch C1, includes first
Driving disc spacing pressing and the first clutch plate, with the connection of spline slide and moment of torsion is transmitted between the first driving disc spacing pressing and the shell of double clutch,
Transmission moment of torsion is splined between first clutch plate and the first input shaft 1, the second automatic clutch C2 includes the second driving disc spacing pressing
With the second clutch plate, with the connection of spline slide and moment of torsion is transmitted between the second driving disc spacing pressing and the shell of double clutch, second from
Transmission moment of torsion is splined between Moving plate and the second input shaft 2.First input shaft 1 and the second input shaft 2 are with coaxial package cloth
Put, including the first input shaft 1, outside, the first input shaft 1 stretches out the second input shaft 2 in one end away from double clutch (C1, C2)
Second input shaft 2.One is fixed with successively on first input shaft 1 from one end away from double clutch to reverse gear driving gear 11, five
Seven gear driving gears 15, three keep off driving gears 13, wherein a gear shared one reverses gear driving gear 11 with reversing gear, five gears with seven gears altogether
With five or seven gear driving gears 15.Six gear driving gears are fixed with successively from one end away from double clutch on second input shaft 2
26th, four gear driving gears 24, two gear driving gear 22.Correspondingly, on the first output shaft 3 from one end away from double clutch
A gear driven gear 31, five gear driven gear 35, six is set with successively and keeps off the gear driven gear 32 of driven gear 36, two, second
On output shaft 4 from away from double clutch one end be set with successively reverse gear driven gear 49, seven keep off driven gear 47, three gear from
Moving gear 43, four keeps off driven gear 44.There are a gear synchronizer S1, five gear synchronizer S5, six gear synchronizers on first output shaft 3
S6, two gear synchronizer S2, eight, which keep off synchronizer S8, is fixed on five gear driven gears 35 and can be connect with six gear driven gears 36
Close and separate, also have reverse gear synchronizer SR, seven gear synchronizer S7, three gear synchronizer S3, four gear synchronizers on the second output shaft 4
S4.First output shaft 3 is fixed with the first main deceleration driving gear 30 close to one end of double clutch, and the second output shaft 4 is close to double
One end of clutch is further fixed on 600 and second main deceleration driving gear 40 of parking ratchet wheel, the first main deceleration driving gear 30,
Two main deceleration driving gears 40 are engaged with final gear 50 at the same time, and shell of the final gear 50 then with differential mechanism 5 is fixedly connected,
Last power is delivered on the wheel on both sides by the semiaxis 9 of 5 both sides of differential mechanism.The effect of this arrangement is axially only to arrange
7 gear pairs and 3 synchronizers, axial dimension is compact, and easy to distribute each gear speed ratio, gear life is high.
Apart from double clutch distalmost end a gear is fixed on the first input shaft 1 and shared one of reversing gear is reversed gear driving gear
11, on the first output shaft 3 suit with this one reverse gear that driving gear 11 is meshed one keep off driven gear 31 and be disposed with corresponding
One gear synchronizer S1, reversing gear of being meshed with a gear driven gear 31 is set with the second output shaft 4 and driven gear 49 and is arranged
There is corresponding reverse gear synchronizer SR.The benefit of this arrangement is to reverse gear and 1 gear arranges the same end of speed changer, close to bearing,
Stress is best, and avoid positioned at the speed changer other end differential mechanism 5 and 1 gear driven gear 31 or the driven gear 49 that reverses gear it is dry
The possibility related to.In addition, this arrangement is avoided using reverse gear shaft, only 4 axis so that radial dimension is minimum.
Five or the seven gear driving gears 15 that five gears and seven gears share are fixed with the first input shaft 1, are covered on the first output shaft 3
Equipped with five or the seven gear driving gears 15 that five gears and seven gears share are meshed five keeps off driven gears 35 and be disposed with corresponding five
Synchronizer S5 is kept off, seven gears being meshed with five or the seven gear driving gears 15 that five gears and seven gears share are set with the second output shaft 4
Driven gear 47 is simultaneously disposed with corresponding seven gear synchronizers S7.The benefit of this arrangement be five gears and seven gear be high gear, it
Share five or seven gear driving gears 15, be conducive to Speed Ratio Distribution and design of gears, and since speed is smaller, five or seven gear driving tooths
Take turns 15 larger, advantageously ensure that intensity and the service life of driving gear 15.
In other embodiments, the parking ratchet wheel can also be arranged on first output shaft or the differential mechanism
On.
Specific power transmission line is described as follows：
During vehicle start, transmission gear is a gear, the mode of realization be gear shifting actuating mechanism by a gear synchronizer S1 with
One gear driven gear 31 engages, then the first automatic clutch C1 is engaged, while the second automatic clutch C2 separation is (for normally closed
Its state of formula clutch is changed into separating from engagement, and for normally open clutch, then its state keeps separation).Turn of engine at this time
Square is delivered to the first input shaft 1 by the first automatic clutch C1, then passes to a gear driven tooth through the driving gear 11 that reverses gear
Wheel 31, is then delivered to the first output shaft 3 by a gear synchronizer S1, and being delivered to master by the first main deceleration driving gear 30 subtracts
Fast gear 50, is finally delivered on the semiaxis and wheel of both sides via differential mechanism 5.
As vehicle continues to accelerate, when reaching the shifting points of two gear of gear liter, gear shifting actuating mechanism keeps off synchronizer S2 by two
Engaged with two gear driven gears 32, then the second automatic clutch C2 is engaged, while the first automatic clutch C1 is separated, first
After automatic clutch C1 is kept completely separate, gear shifting actuating mechanism disengages a gear synchronizer S1 and a gear driven gear 31.Send out at this time
The torque of motivation is delivered to the second input shaft 2 by the second automatic clutch C2, then passes to two gears through two gear driving gear 22
Driven gear 32, is then delivered to the first output shaft 3 by two gear synchronizer S2, is transmitted by the first main deceleration driving gear 30
To final gear 50, finally it is delivered to via differential mechanism 5 on the semiaxis and wheel of both sides.
As vehicle continues to accelerate, when reaching the shifting points of two gears liter, three gear, gear shifting actuating mechanism keeps off synchronizer S3 by three
Engaged with three gear driven gears 43, then the first automatic clutch C1 is engaged, while the second automatic clutch C2 is separated, second
After automatic clutch C2 is kept completely separate, gear shifting actuating mechanism disengages two gear synchronizer S2 and two gear driven gears 32.Send out at this time
The torque of motivation is delivered to the first input shaft 1 by the first automatic clutch C1, then passes to three gears through three gear driving gears 13
Driven gear 43, is then delivered to the second output shaft 4 by three gear synchronizer S3, is transmitted by the second main deceleration driving gear 40
To final gear 50, finally it is delivered to via differential mechanism 5 on the semiaxis and wheel of both sides.
As vehicle continues to accelerate, when reaching the shifting points of three gears liter, four gear, gear shifting actuating mechanism keeps off synchronizer S4 by four
Engaged with four gear driven gears 44, then the second automatic clutch C2 is engaged, while the first automatic clutch C1 is separated, first
After automatic clutch C1 is kept completely separate, gear shifting actuating mechanism disengages three gear synchronizer S3 and three gear driven gears 43.Send out at this time
The torque of motivation is delivered to the second input shaft 2 by the second automatic clutch C2, then passes to four gears through four gear driving gears 24
Driven gear 44, is then delivered to the second output shaft 4 by four gear synchronizer S4, is transmitted by the second main deceleration driving gear 40
To final gear 50, finally it is delivered to via differential mechanism 5 on the semiaxis and wheel of both sides.
As vehicle continues to accelerate, when reaching the shifting points of four gears liter, five gear, gear shifting actuating mechanism keeps off synchronizer S5 by five
Engaged with five gear driven gears 35, then the first automatic clutch C1 is engaged, while the second automatic clutch C2 is separated, second
After automatic clutch C2 is kept completely separate, gear shifting actuating mechanism disengages four gear synchronizer S4 and four gear driven gears 44.Send out at this time
The torque of motivation is delivered to the first input shaft 1 by the first automatic clutch C1, then passes to five through five or seven gear driving gears 15
Driven gear 35 is kept off, then the first output shaft 3 is delivered to by five gear synchronizer S5, is passed by the first main deceleration driving gear 30
Final gear 50 is delivered to, is finally delivered to via differential mechanism 5 on the semiaxis and wheel of both sides.
As vehicle continues to accelerate, when reaching the shifting points of five gears liter, six gear, gear shifting actuating mechanism keeps off synchronizer S6 by six
Engaged with six gear driven gears 36, then the second automatic clutch C2 is engaged, while the first automatic clutch C1 is separated, first
After automatic clutch C1 is kept completely separate, gear shifting actuating mechanism disengages five gear synchronizer S5 and five gear driven gears 35.Send out at this time
The torque of motivation is delivered to the second input shaft 2 by the second automatic clutch C2, then passes to six gears through six gear driving gears 26
Driven gear 36, is then delivered to the first output shaft 3 by six gear synchronizer S6, is transmitted by the first main deceleration driving gear 30
To final gear 50, finally it is delivered to via differential mechanism 5 on the semiaxis and wheel of both sides.
As vehicle continues to accelerate, when reaching the shifting points of six gears liter, seven gear, gear shifting actuating mechanism keeps off synchronizer S7 by seven
Engaged with seven gear driven gears 47, then the first automatic clutch C1 is engaged, while the second automatic clutch C2 is separated, second
After automatic clutch C2 is kept completely separate, gear shifting actuating mechanism disengages six gear synchronizer S6 and six gear driven gears 36.Send out at this time
The torque of motivation is delivered to the first input shaft 1 by the first automatic clutch C1, then passes to seven gears through seven gear driving gears 15
Driven gear 47, is then delivered to the second output shaft 4 by seven gear synchronizer S7, is transmitted by the second main deceleration driving gear 40
To final gear 50, finally it is delivered to via differential mechanism 5 on the semiaxis and wheel of both sides.
As vehicle continues to accelerate, when reaching the shifting points of seven gears liter, eight gear, gear shifting actuating mechanism keeps off synchronizer S8 by eight
Engaged with six gear driven gears 36, and keep seven gear synchronizer S7 to be remained engaged with seven gear driven gears 47.Again by second certainly
Dynamic clutch C2 engagements, while the first automatic clutch C1 is separated.The torque of engine at this time passes through the second automatic clutch C2
The second input shaft 2 is delivered to, then six gear driven gears 36 are passed to through six gear driving gears 26, then passes through eight gear synchronizer S8
Five gear driven gears 35 are delivered to, five gear driven gears 35 pass to seven gear driven gears 47 by five or seven gear driving gears 15,
Then the second output shaft 4 is passed to by seven gear synchronizer S7, then main deceleration is delivered to by the second main deceleration driving gear 40
Gear 50, is finally delivered on the semiaxis and wheel of both sides via differential mechanism 5.
When vehicle, which is linked into, to reverse gear, the mode of realization is gear shifting actuating mechanism by reverse gear synchronizer SR and the driven gear that reverses gear
49 engagements, then the first automatic clutch C1 is engaged, while the second automatic clutch C2 separation is (for its shape of normally closed type clutch
State is changed into separating from engagement, and for normally open clutch, then its state keeps separation).The torque of engine at this time by first from
Dynamic clutch C1 is delivered to the first input shaft 1, then is delivered to and reversed gear by a gear driven gear 31 through the driving gear 11 that reverses gear
On driven gear 49, then through the driven gear 49 that reversing gear and be delivered to the second output shaft 4, passed by the second main deceleration driving gear 40
Final gear 50 is delivered to, is finally delivered to via differential mechanism 5 on the semiaxis and wheel of both sides.
With vehicle deceleration, when reaching the shifting points of downshift, gear shifting actuating mechanism is first by compared with the synchronizer of low gear and the gear
Driven gear engagement, then will compared with the engagement of low gear corresponding automatic clutch, then will compared with the corresponding automatic clutch separation of high gear,
It will finally be separated compared with the synchronizer of high gear with the driven gear of the gear, only eight gear drops seven make an exception when keeping off.
For example, when vehicle deceleration reach eight gears drop seven gear shifting points when, gear shifting actuating mechanism first will by first automatically from
Clutch C1 is engaged, while the second automatic clutch C2 is separated, then eight gear synchronizer S8 are separated with six gear driven gears 36.
When vehicle continues to slow down, and reaches the shifting points of seven gears drop, six gear, gear shifting actuating mechanism is first by six gear synchronizer S6
Engaged with six gear driven gears 36, then the second automatic clutch C2 is engaged, then separated the first automatic clutch C1, finally
Seven gear synchronizer S7 are separated with seven gear driven gears 47.Following gear will carry out in a similar manner when keeping off.
More preferably, eight fast double-clutch automatic gearboxes can trip stop according to the demand of road conditions, such as directly shift to three from a gear
Gear or four gears or other gears, and for example directly shift to six gears or five gears or other gears from eight gears.
Meanwhile the present invention has other drive paths, it is respectively：
Special bang path 1:Eight gear clutch S8 are engaged with six gear driven gears 36, three gear clutch S3 closures, and first
Automatic clutch C1 is separated, and the second automatic clutch C2 engagements, the power of engine is passed by the second automatic clutch C2 at this time
It is delivered on the second input shaft 2, is delivered to by six gear driving gears 26 on six gear driven gears 36, is passed through eight gear synchronizer S8
It is delivered on five gear driven gears 35, is delivered to by five gear driven gears 35 by five or seven gear driving gears 15 on the first input shaft 1,
First input shaft 1 is delivered to three gear driven gears 43 by three gear driving gears 13, is then delivered to by three gear synchronizer S3
Second output shaft 4, is delivered to final gear 50 by the second main deceleration driving gear 40, is finally delivered to via differential mechanism 5
On the semiaxis and wheel of both sides.
Special bang path 2:Eight gear clutch S8 are engaged with six gear driven gears 36, a gear clutch S1 closures, and first
Automatic clutch C1 is separated, and the second automatic clutch C2 engagements, the power of engine is passed by the second automatic clutch C2 at this time
It is delivered on the second input shaft 2, is delivered to by six gear driving gears 26 on six gear driven gears 36, is passed through eight gear synchronizer S8
It is delivered on five gear driven gears 35, is delivered to by five gear driven gears 35 by five or seven gear driving gears 15 on the first input shaft 1,
First input shaft 1 is delivered to a gear driven gear 31 by the driving gear 11 that reverses gear, and then passes through a gear synchronizer S1 and transmits
To the first output shaft 3, final gear 50 is delivered to by the first main deceleration driving gear 30, is finally transmitted via differential mechanism 5
Onto the semiaxis and wheel of both sides.
Special bang path 3:Eight gear clutch S8 are engaged with six gear driven gears 36, four gear clutch S4 closures, and first
Automatic clutch C1 is engaged, and the second automatic clutch C2 separation, the power of engine is passed by the first automatic clutch C1 at this time
It is delivered on the first input shaft 1, is delivered to by five or seven gear driving gears 15 on five gear driven gears 35, through eight gear synchronizer S8
It is delivered on six gear driven gears 36, is delivered to by six gear driven gears 36 by six gear driving gears 26 on the second input shaft 2,
Second input shaft 2 is delivered to two gear driven gears 32 by two gear driving gear 13, is then delivered to by two gear synchronizer S2
Second output shaft 4, is delivered to final gear 50 by the second main deceleration driving gear 40, is finally delivered to via differential mechanism 5
On the semiaxis and wheel of both sides.
Special bang path 4:Eight gear clutch S8 are engaged with six gear driven gears 36, two gear clutch S2 closures, and first
Automatic clutch C1 is engaged, and the second automatic clutch C2 separation, the power of engine is passed by the first automatic clutch C1 at this time
It is delivered on the first input shaft 1, is delivered to by five or seven gear driving gears 15 on five gear driven gears 35, through eight gear synchronizer S8
It is delivered on six gear driven gears 36, is delivered to by six gear driven gears 36 by six gear driving gears 26 on the second input shaft 2,
Second input shaft 2 is delivered to two gear driven gears 32 by two gear driving gear 22, is then delivered to by two gear synchronizer S2
First output shaft 3, is delivered to final gear 50 by the first main deceleration driving gear 30, is finally delivered to via differential mechanism 5
On the semiaxis and wheel of both sides.
Above-mentioned 4 kinds of special bang paths are since speed is more close to some gear between eight gears than a gear, or are switched to spy
It can not ensure that power does not interrupt during different bang path, therefore only be used under special operation condition.
In the present invention, only five gears and seven gears share driving gear, and the design of the gear speed ratio in addition to eight keep off is from five gears
With seven gear speed than influencing, be conducive to the design of transmission gear ratio.
Embodiment 2
As shown in Fig. 2, compared with Example 1, eight fast double-clutch automatic gearboxes shown in embodiment 2 difference lies in：The
Four gear driving gears 24, six gear driving gear 26, two is fixed with successively on two input shafts 2 from one end away from double clutch to keep off
Driving gear 22, four gear driven gears 34, which correspond to, to be sleeved on the first output shaft 3, and six gear driven gears 46, which correspond to, is sleeved on second
On output shaft 4；Correspondingly, four gear synchronizer S4 are located on the first output shaft 3, six gear synchronizer S6 are located on the second output shaft 4,
Eight gear synchronizer S8 are fixed on five gear driven gears 35 and can engage and separate with four gear driven gears 34；In this way, can
To ensure eight gear speed, frequently seven gear speed are than small, to meet actual requirement.
In other embodiments, it is also arranged so that：It is solid successively from one end away from double clutch on second input shaft 2
Surely there is two gear driving gear 22, four to keep off driving gear 24, six and keep off driving gear 26.That is, two gears on the second input shaft 2
Transposition between any two gear between driving gear, four gear driven gears and six gear driven gears.
Above example is referring to the drawings, to a preferred embodiment of the present invention will be described in detail.Those skilled in the art
Member by above-described embodiment carry out various forms on modification or change, but without departing substantially from the present invention essence in the case of, all
Fall within the scope and spirit of the invention.
Claims (5)
1. eight fast double-clutch automatic gearbox of one kind, it is characterised in that including double clutch, the first input shaft, the second input shaft,
First output shaft, the second output shaft and differential mechanism,
The double clutch includes the first automatic clutch and the second automatic clutch, between two input shafts and two output shafts
Mutually be arranged in parallel, first input shaft is connected with first automatic clutch, second input shaft with it is described
Second automatic clutch is connected, and first input shaft is arranged with second input shaft with coaxial package, and described first is defeated
Including entering axis, outside, first input shaft is defeated in one end stretching described second away from double clutch for second input shaft
Enter axis；
Be fixed with first input shaft one reverse gear driving gear, five or seven gear driving gears, three gear driving gears, one gear and fall
Gear shares one and reverses gear driving gear, and five gears share five or seven gear driving gears with seven gears；Six gears are fixed with second input shaft
Driving gear, four gear driving gears, two gear driving gear；Correspondingly, be set with first output shaft gear driven gear,
Any two in five gear driven gears and six gear driven gears, two gear driven gears, four gear driven gears, described second is defeated
The driven gear that reverses gear, seven gear driven gears, three gear driven gears and six gear driven gears, two gear driven tooths are set with shaft
One on the first output shaft is not arranged in wheel, four gear driven gears；First output shaft is equipped with a gear synchronizer, five gears
Any two in synchronizer and six gear synchronizers, two gear synchronizers, four gear synchronizers, second output shaft are equipped with
Keep off in synchronizer, seven gear synchronizers, three gear synchronizers, six gear synchronizers, two gear synchronizers and four gear synchronizers and be not arranged on first
One on output shaft, and eight gear synchronizers are equipped with five gear driven gears, described eight keep off synchronizer and arranged on described first
Six gear driven gears or four gear driven gears or two gear driven gear engagements and separation on output shaft；First output shaft leans on
One end of nearly double clutch is fixed with the first main deceleration driving gear, and second output shaft is fixed close to one end of double clutch
There is the second main deceleration driving gear, the first main deceleration driving gear, the second main deceleration driving gear are led with one at the same time
Reduction gearing engages, which is fixed on the differential mechanism.
2. according to claim 1 eight fast double-clutch automatic gearboxes, it is characterised in that：Described one reverses gear driving gear cloth
Corresponding suit is put on first input shaft in double clutch distalmost end, first output shaft one to reverse gear actively with this
The gear driven gear that gear is meshed, and corresponding gear synchronizer is disposed with, accordingly covered on second output shaft
Equipped with the driven gear that reverses gear being meshed with described one gear driven gear, and it is disposed with corresponding reverse gear synchronizer.
3. according to claim 2 eight fast double-clutch automatic gearboxes, it is characterised in that：Five or the seven gear driving gear cloth
It is placed in one to reverse gear between driving gear and six gear driving gears or four gear driven gears or two gear driven gears, first output
Five gear driven gears being meshed with described 57 gear driving gears are set with axis and are disposed with corresponding five and keep off synchronizer, institute
State and seven gear driven gears being meshed with described 57 gear driving gears are set with the second output shaft and are disposed with corresponding seven
Keep off synchronizer；It is described eight gear synchronizer be fixed on it is described five gear driven gear on and with described six gear driven gears or four gear from
Moving gear or two gear driven gear engagements and separation.
4. according to claim 1 eight fast double-clutch automatic gearboxes, it is characterised in that：The first automatic clutch bag
Include the first driving disc spacing pressing and the first clutch plate, between the shell of first driving disc spacing pressing and double clutch with the connection of spline slide simultaneously
Moment of torsion is transmitted, transmission moment of torsion is splined between first clutch plate and first input shaft；Described second automatically from
Clutch includes the second driving disc spacing pressing and the second clutch plate, with spline slide between the shell of second driving disc spacing pressing and double clutch
Connect and transmit moment of torsion, transmission moment of torsion is splined between second clutch plate and second input shaft.
5. according to claim 1 eight fast double-clutch automatic gearboxes, it is characterised in that：Parking ratchet wheel is further included, it is described
Parking ratchet wheel is arranged on first output shaft or on second output shaft or on the differential mechanism.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610878119.8A CN107917167A (en) | 2016-10-09 | 2016-10-09 | Eight fast double-clutch automatic gearboxes |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610878119.8A CN107917167A (en) | 2016-10-09 | 2016-10-09 | Eight fast double-clutch automatic gearboxes |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107917167A true CN107917167A (en) | 2018-04-17 |
Family
ID=61892099
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610878119.8A Pending CN107917167A (en) | 2016-10-09 | 2016-10-09 | Eight fast double-clutch automatic gearboxes |
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| CN108397523A (en) * | 2018-05-11 | 2018-08-14 | 广州汽车集团股份有限公司 | Double-clutch speed changer |
| CN111623092A (en) * | 2019-02-28 | 2020-09-04 | 长城汽车股份有限公司 | Double-clutch transmission and vehicle |
| CN113669418A (en) * | 2020-05-14 | 2021-11-19 | 广州汽车集团股份有限公司 | Eight-speed automatic transmission and vehicle |
| CN113685504A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685497A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685506A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685499A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685509A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685508A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113915298A (en) * | 2020-07-08 | 2022-01-11 | 广州汽车集团股份有限公司 | Vehicle automatic gearbox and vehicle |
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| CN113685508A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685506A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685499A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685509A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685497A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685504B (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 |
| CN113685508B (en) * | 2020-05-18 | 2024-01-26 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685499B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685506B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
| CN113685504A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685497B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
| CN113685509B (en) * | 2020-05-18 | 2024-03-29 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113915298A (en) * | 2020-07-08 | 2022-01-11 | 广州汽车集团股份有限公司 | Vehicle automatic gearbox and vehicle |
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