CN106321748A - Eight-speed double clutch speed change device - Google Patents
Eight-speed double clutch speed change device Download PDFInfo
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- CN106321748A CN106321748A CN201610887296.2A CN201610887296A CN106321748A CN 106321748 A CN106321748 A CN 106321748A CN 201610887296 A CN201610887296 A CN 201610887296A CN 106321748 A CN106321748 A CN 106321748A
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/02—Selector apparatus
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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
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention provides an eight-speed double clutch speed change device, and belongs to the technical field of transmissions. The speed change device comprises a main input shaft, a first input device, a second input device, a double clutch, a first output device, a second output device, a third output device and a plurality of synchronizers. The first input device comprises a first input shaft and three odd-gear driving gears. The second input device comprises a second input shaft and two even-gear driving gears. The first output device comprises a first output shaft and four driven gears arranged on the first output shaft. One of the three odd-gear driving gears is a common driving gear engaged with two driven gears. Each of the two even-gear driving gears is a common driving gear engaged with two driven gears. One of the four driven gears on the first output shaft serves as a reverse-gear middle idle gear. The speed change device is small in axial length, wide in reverse-gear gear layout and speed ratio range and wide in parking ratchet wheel layout range.
Description
Technical field
The present invention relates to dual-clutch transmission technical field, particularly relate to a kind of eight speed double-clutch speed change gears.
Background technology
The double clutch speed variator of many gears has more advantage in terms of promoting transmission efficiency and quick and stable gear shift.Many gears
Ratio coverage, the speed ratio of each adjacent gear positions and rank can be increased than being distributed wide ranges, be conducive to promoting low speed climbing capacity, reduce
The Acceleration of starting time, improve transmission efficiency, promote the rapid stationarity of gear shift, thus ensure acceleration and the comfortableness of vehicle, real
The dynamic property of existing vehicle and economy.
Traditional eight-speed transmissions device transmission efficiency ratio is relatively low, and existing eight-speed transmissions device is first due to driving gear
More and cause axial dimension longer, it is not easy to the layout of vehicle engine assembly；Second driving tooth is shared when partial gear uses
During wheel, although can relatively reduce the axial dimension of variator, but gear-driven speed ratio error may be bigger, it is more difficult to realize institute
Desired speed ratio；Three due to back gear acceptor center away from or the impact of shared gear ratio, back gear layout and speed ratio select
It is limited in scope.
Summary of the invention
The present invention is to solve that the speed change gear casing existing for eight speed double-clutch speed change gears of prior art is axial
Length is longer, and vehicle engine assembly is arranged limited, and back gear layout and the speed ratio range of choice are limited, and parking ratchet wheel arranges scope
The problem of limited grade, it is provided that a kind of axial length is shorter, back gear layout and ratio coverage is wide, parking ratchet wheel layout scope is wide
Eight speed double-clutch speed change gears.
It is an object of the present invention to provide a kind of eight speed double-clutch speed change gears, including:
For receiving the primary input axle of motor torque；
First input equipment, including the first power shaft for rotating coaxially with described primary input axle be arranged on described
Three odd number shelves driving gears at one power shaft；
Secondary input device, including for rotating coaxially with described primary input axle and at least partially around described first defeated
Enter the second power shaft of axle and be arranged on two even gear driving gears at described second power shaft；
Double clutch, described double clutch includes for the torque of primary input axle optionally being passed to described first defeated
Enter axle and the first clutch of described second power shaft and second clutch；
First output device, including parallel with described primary input axle and arranged apart with described primary input between centers first defeated
Shaft and be arranged on four driven gears at the first output shaft, four driven gears at described first output shaft all can select
Selecting property it is connected to described first output shaft with common rotation；
Second output device, including parallel with described primary input axle and arranged apart with described primary input between centers second defeated
Shaft and be arranged on four driven gears at the second output shaft, four driven gears at described second output shaft all can select
Selecting property it is connected to described second output shaft with common rotation；
3rd output device, including parallel with described primary input axle and arranged apart with described primary input between centers the 3rd defeated
Shaft and be arranged on the reverse gear driven gear at the 3rd output shaft, described reverse gear driven gear can be used to selectively connect to described
3rd output shaft is with common rotation；
Multiple lock units, the plurality of lock unit is for by least one in all driven gears and described first output
At least one in axle, the second output shaft and the 3rd output shaft is selectively connected；
Wherein, one in described three odd number shelves driving gears is the shared driving tooth engaged with two driven gears
Wheel, each of which of said two even gear driving gear is the shared driving gear engaged with two driven gears, described the
One in four driven gears at one output shaft is engaged with described reverse gear driven gear as reverse gear intermediate idler.
Further, three odd number shelves driving gears at described first power shaft be respectively one grade of driving gear, three or five
Shelves driving gear and seven grades of driving gears, described three or five grades of driving gears are the shared driving gear of third gear and five grades；
Four driven gears at described first output shaft be respectively first speed driven gear, two grades of driven gears, third gear from
Moving gear and six grades of driven gears；
Four driven gears at described second output shaft be respectively fourth gear driven gear, five grades of driven gears, seven grades from
Moving gear and eight grades of driven gears.
Further, described three the odd number shelves driving gears at described first power shaft relative to described double clutch by
Proximal and distal order is three or five grades of driving gears, one grade of driving gear and seven grades of driving gears successively；
Wherein, described three or five grades of driving gears engage with described third gear driven gear and described five grades of driven gears respectively；
Described one grade of driving gear engages with described first speed driven gear；
Described seven grades of driving gears engage with described seven grades of driven gears.
Further, the plurality of lock unit include a third gear lock unit, two or six grades of lock units, four or eight grades of lock units, five
Seven grades of lock units and reversing-gear synchronizer；
A described third gear lock unit is arranged at described first output shaft, for by first speed driven gear and third gear driven tooth
Wheel is used to selectively connect to described first output shaft；
Described two or six grades of lock units are arranged at described first output shaft, for by two grades of driven gears and six grades of driven tooth
Wheel is used to selectively connect to described first output shaft；
Described four or eight grades of lock units are arranged at described second output shaft, for by fourth gear driven gear and eight grades of driven tooth
Wheel is used to selectively connect to described second output shaft；
Described five or seven grades of lock units are arranged at described second output shaft, for by five grades of driven gears and seven grades of driven tooth
Wheel is used to selectively connect to described second output shaft；
Described reversing-gear synchronizer is arranged at described 3rd output shaft, for being used to selectively connect to by reverse gear driven gear
Described 3rd output shaft.
Further, three odd number shelves driving gears at described first power shaft are respectively one grade of driving gear, third gear
Driving gear and five or seven grades of driving gears, described five or seven grades of driving gears are the shared gear of five grades and seven grades；
Four driven gears at described first output shaft be respectively first speed driven gear, two grades of driven gears, five grades from
Moving gear and six grades of driven gears；
Four driven gears at described second output shaft be respectively third gear driven gear, fourth gear driven gear, seven grades from
Moving gear and eight grades of driven gears.
Further, described three the odd number shelves driving gears at described first power shaft relative to described double clutch by
Proximal and distal order is five or seven grades of driving gears, one grade of driving gear and third speed drive gear successively；
Wherein, described five or seven grades of driving gears engage with described five grades of driven gears and described seven grades of driven gears respectively；
Described one grade of driving gear engages with described first speed driven gear；
Described third speed drive gear engages with described third gear driven gear.
Further, the plurality of lock unit include a Five-gear synchronizer, two or six grades of lock units, Radix Notoginseng shelves lock unit, four
Eight grades of lock units and reversing-gear synchronizer；
A described Five-gear synchronizer is arranged at described first output shaft, for by first speed driven gear and five grades of driven tooth
Wheel is used to selectively connect to described first output shaft；
Described two or six grades of lock units are arranged at described first output shaft, for by two grades of driven gears and six grades of driven tooth
Wheel is used to selectively connect to described first output shaft；
Described Radix Notoginseng shelves lock unit is arranged at described second output shaft, for by third gear driven gear and seven grades of driven tooth
Wheel is used to selectively connect to described second output shaft；
Described four or eight grades of lock units are arranged at described second output shaft, for by fourth gear driven gear and eight grades of driven tooth
Wheel is used to selectively connect to described second output shaft；
Described reversing-gear synchronizer is arranged at described 3rd output shaft, for being used to selectively connect to by reverse gear driven gear
Described 3rd output shaft.
Further, two even gear driving gears at described second power shaft are respectively two fourth gear driving gears and six
Eight grades of driving gears, described two fourth gear driving gears are the shared gear of two grades and fourth gear, and described six or eight grades of driving gears are six
Shelves and the shared gear of eight grades；
Described two fourth gear driving gears engage with described two grades of driven gears and described fourth gear driven gear respectively；
Described six or eight grades of driving gears engage with described six grades of driven gears and described eight grades of driven gears respectively.
Further, described reverse gear driven gear engages with described two grades of driven gears, so that described two grades of driven tooth
Wheel is as described reverse gear intermediate idler；
Alternatively, described reverse gear driven gear engages with described first speed driven gear, so that described first speed driven gear
As described reverse gear intermediate idler.
Further, it is additionally provided with parking ratchet wheel at described 3rd output shaft；
Described first output device also includes being arranged on the main deceleration output gear of first at the first output shaft；
Described second output device also includes being arranged on the main deceleration output gear of second at the second output shaft；
Described 3rd output device also includes the 3rd main deceleration output gear being arranged at the 3rd output shaft；
Described device also includes and described first main deceleration output gear, the second main deceleration output gear and the 3rd main deceleration
The main reduction driven gear that output gear connects jointly.
Alternatively, it is to be connected by needle bearing between all driven gears with corresponding output shaft；
Further, it is connected by spline between all lock units with corresponding output shaft.
The eight speed double-clutch speed change gears of the present invention are owing to realizing under desired speed ratio premise, on power shaft in guarantee
Driving gear use shared gear train to greatest extent, reduce number of teeth quantity so that its structure is compacter, the length of assembly
Shorter.According to the solution of the present invention, owing to being cancelled from the first or second output shaft by parking ratchet wheel, and it is arranged into the 3rd
On output shaft, thus the first or second output shaft length shortens, and not only makes the first or second output shaft rigidity reinforced, and makes
Obtain parking ratchet wheel layout scope and become wide, and then make whole halting mechanism layout scope become wide.Additionally, by reverse gear driven gear cloth
Office, on the 3rd output shaft, is not affected by power shaft and the first or second output shaft centre-to-centre spacing, and back gear layout is cleverer
Living, the speed ratio range of choice is wider.This double each gear layout of clutch speed variator of eight speed is simple, and cost is relatively low, it is possible to existing
Seven speed speed change gears on simply transform and can realize.
According to below in conjunction with the accompanying drawing detailed description to the specific embodiment of the invention, those skilled in the art will be brighter
Above-mentioned and other purposes, advantage and the feature of the present invention.
Accompanying drawing explanation
Describe some specific embodiments of the present invention the most by way of example, and not by way of limitation in detail.
Reference identical in accompanying drawing denotes same or similar parts or part.It should be appreciated by those skilled in the art that these
Accompanying drawing is not necessarily drawn to scale.In accompanying drawing:
Fig. 1 is the schematic diagram of the eight speed double-clutch speed change gears according to first embodiment of the invention.
Detailed description of the invention
Fig. 1 shows the schematic diagram of eight speed double-clutch speed change gears according to an embodiment of the invention, and this speed change fills
Put and can include primary input axle and final gear assembly.This primary input axle is continuously connected to electromotor or other moments of torsion produce
Device is to provide driving torque to this primary input axle.This final gear assembly is rotatably driven differential assembly 60.Differential
Moment of torsion by final gear component passes is finally delivered to a pair wheel of vehicle by device assembly 60.
Speed change gear generality can include various axle, driving tooth wheels, driven tooth wheels, double clutch 70 and can select
The lock unit that selecting property engages.
Axle can include that first power shaft the 11, second power shaft the 21, first output shaft the 31, second output shaft 41 and the 3rd is defeated
Shaft 51.Wherein, the first power shaft 11 and the second power shaft 21 all rotate coaxially with primary input axle.Second power shaft 21 is hollow
, it is concentric with the first power shaft 11 and can be socketed on the first power shaft 11.First output shaft the 31, second output shaft 41 and
Three output shafts 51 each parallel to primary input axle and and primary input axle between there is certain distance.First output shaft 31 and the second output
Axle 41 lays respectively at the both sides of primary input axle, and the first output shaft 31 is between the 3rd output shaft 51 and the first power shaft 11.
Double clutch 70 can include first clutch 71 and second clutch 72, double clutch 70 can optionally by
The power that electromotor transmission comes passes to the first power shaft 11 by first clutch 71, or is passed to by second clutch 72
Second power shaft 21.Specifically, first clutch 71 is connected with the first power shaft 11, second clutch 72 and the second power shaft
21 are connected, and when first clutch 71 is in engagement state and second clutch 72 is in released state, electromotor transmission comes
Power can pass to the first power shaft 11 by first clutch 71, and is in released state and second at first clutch 71
When clutch 72 is in engagement state, the power that electromotor transmission comes can pass to the second power shaft by second clutch 72
21。
It should be appreciated that the specific configuration of double clutch 70 and operation principle have been the common knowledges of this area, because of
This for purposes of brevity, specific configuration and operation principle to double clutch 70 do not elaborate.
Driving tooth wheels include being arranged on three odd number shelves driving gears at the first power shaft 11 and to be arranged on second defeated
Enter two even gear driving gears at axle 21.According to the present invention program, the first input equipment 10 includes the first power shaft 11 He
It is arranged on three odd number shelves driving gears at described first power shaft 11.Secondary input device 20, including the second power shaft 21
With two the even gear driving gears being arranged at described second power shaft 21.
According to a first embodiment of the invention, three odd number shelves driving gears are one grade of driving gear 13,35 respectively
Shelves driving gear 14 and seven grades of driving gears 12.It is understandable that the shared tooth that three or five grades of driving gears 14 are third gear and five grades
Wheel.Specifically, these three odd number shelves driving gears are arranged at the first power shaft 11 as follows, with reference to the setting of Fig. 1
Mode, according to the order from the close-by examples to those far off of the distance between double clutch be: 14, one grade of driving gear 13 of three or five grades of driving gears
With seven grades of driving gears 12.These three odd number shelves driving gears all can along with the first power shaft 11 synchronous rotary, such as this three
Individual odd number shelves driving gear all can be coordinated by spline and the first power shaft 11.In another embodiment, these three odd number shelves
Driving gear is all formed in one with the first power shaft 11.In other embodiments, these three odd number shelves driving gears and first
Can also be it can be made to connect by the way of coordinating by other between power shaft 11.
These two even gear driving gears are two fourth gear driving gears 22 and six or eight grades of driving gears 23 respectively.It is appreciated that
Be two fourth gear driving gears 22 be the shared gear of two grades and fourth gear, six or eight grades of driving gears 23 are six grades and eight grades share
Gear.Specifically, these two even gear driving gears are arranged at the second power shaft 21 as follows, setting with reference to Fig. 1
Put mode, according to the order from the close-by examples to those far off of the distance between double clutch 70 be: two fourth gear driving gears 22 and six or eight grades of masters
Moving gear 23.These two even gear driving gears all can be along with the second power shaft 21 synchronous rotary.These two even gear are actively
Gear all can be along with the second power shaft 21 synchronous rotary, and such as these two even gear driving gears all can be by spline and the
Two power shafts 21 coordinate.In another embodiment, these two even gear driving gears are all formed in one with the second power shaft 21.
In other embodiments, can also be can to make it by other between this two even gear driving gears and second power shaft 21
The mode coordinated connects.
Driven tooth wheels include being arranged on four driven gears at the first output shaft 31, are arranged at the second output shaft 41
Four driven gears and be arranged on the reverse gear driven gear 53 at the 3rd output shaft 51.According to the present invention program, the first output
Device 30 includes the first output shaft 31 and is arranged on four driven gears at the first output shaft 31, at described first output shaft 31
Four driven gears all can be used to selectively connect to described first output shaft 31 with common rotation.Second output device
40, including the second output shaft 41 be arranged on four driven gears at the second output shaft 41.3rd output device 50, including
Three output shafts 51 and be arranged on the reverse gear driven gear 53 at the 3rd output shaft 51.
According to a first embodiment of the invention, be arranged on four driven gears at the first output shaft 31 include one grade from
32, two grades of driven gears 35 of moving gear, third gear driven gear 33 and six grades of driven gears 34.Specifically, these four driven gears
It is arranged on as follows at the first output shaft 31, sees Fig. 1, draw near according to the distance between double clutch 70
Order is: first speed driven gear 32,33, six grades of driven gears 34 of third gear driven gear and two grades of driven gears 35.These four from
Moving gear all can relatively rotate relative to the first output shaft 31.These four driven gears are respectively by needle bearing and the first output
Axle 31 is connected, but is not limited to this.
Thus, first speed driven gear 32 engages with one grade of driving gear 13 thus constitutes one grade of gear pair, two grades of driven tooth
Wheel 35 engages with two fourth gear driving gears 22 thus constitutes intermediate gear pair, third gear driven gear 33 and three or five grades of driving gears 14
Engagement thus to constitute third gear secondary, six grades of driven gears 34 engage with six or eight grades of driving gears 23 thus constitute six shift of gears
Secondary.
Be arranged on four driven gears at the second output shaft 41 include 45, five grades of driven gears 43 of fourth gear driven gear,
Seven grades of driven gears 42 and eight grades of driven gears 44.Specifically, to be arranged on second as follows defeated for these four driven gears
At shaft 41, seeing Fig. 1, the order drawn near according to the distance between double clutch 70 is: seven grades of driven gears 42, five
Shelves 43, eight grades of driven gears 44 of driven gear and fourth gear driven gear 45.These four driven gears all can be relative to the first output
Axle 31 relatively rotates.These four driven gears are connected by needle bearing and the first output shaft 31 respectively, but are not limited to this.
Thus, fourth gear driven gear 45 engages with two fourth gear driving gears 22 thus constitutes fourth gear pair, and five grades driven
Gear 43 engages with three or five grades of driving gears 14 thus constitutes five grades of gear pairs, seven grades of driven gears 42 and seven grades of driving gears 12
Engagement thus constitute seven grades of gear pairs, eight grades of driven gears 44 engage with six or eight grades of driving gears 23 thus constitute eight grades of gears
Secondary.Owing to intermediate gear is secondary and fourth gear pair can share two fourth gear driving gears 22, third gear pair and five grades of gear pairs
Three or five grades of driving gears 14, six step tooth wheel set and eight grades of gear pairs can be shared and can share six or eight grades of driving gears 23, altogether may be used
To reduce by three driving gears so that speed change gear compact conformation, assembly length shortens, it is simple to the layout of vehicle engine assembly.
Owing to realizing under desired speed ratio premise in guarantee, the driving gear on power shaft uses shared gear train to greatest extent,
Reduce number of teeth quantity so that its structure is compacter, and the length of assembly is shorter.
Being arranged on the reverse gear driven gear 53 at the 3rd output shaft 51, this reverse gear driven gear 53 is by needle bearing and the
Three output shafts 51 are connected, but are not limited to this.Reverse gear driven gear 53 engages with two grades of driven gears 35, so that two grades of driven tooth
Wheel 35 engages with reverse gear driven gear 53 as reverse gear intermediate idler, and two fourth gear driving gears 22 are the most now as reverse gear the most actively
Gear.In another embodiment, reverse gear driven gear 53 engages with first speed driven gear 32, so that described first speed driven gear
32 engage with reverse gear driven gear 53 as reverse gear intermediate idler, and one grade of driving gear 13 is the most now as reverse gear driving tooth
Wheel.But it is not limited to this.According to the present invention program, by reverse gear driven gear 53 layout to the 3rd output shaft 51, not by power shaft
With the impact of the first or second output shaft 41 centre-to-centre spacing, back gear layout is more flexible, and the speed ratio range of choice is wider.
As it is shown in figure 1, be additionally provided with parking ratchet wheel 52 at the 3rd output shaft 51, parking ratchet wheel 52 is arranged in the 3rd output
On any position arranged of axle 51.In another embodiment, parking ratchet wheel 52 is along first output shaft the 31, second output shaft 41
Or the 3rd the axial location of output shaft 51 can change according to available encapsulated space.According to the solution of the present invention, owing to staying
Car ratchet 52 is cancelled from the first or second output shaft 41, and is arranged on the 3rd output shaft 51, and thus first or second
Output shaft 41 length shortens, and not only makes the first or second output shaft 41 rigidity reinforced, and makes parking ratchet wheel 52 layout model
Enclose change wide, and then make whole halting mechanism layout scope become wide.
According to first embodiment of the invention, speed change gear also includes five lock units, and these five lock units are respectively
One third gear lock unit 310,26 grades lock unit 320,48 grades of lock units 420,57 grades of lock units 410 and reversing-gear synchronizers
510.One third gear lock unit 310 and two or six grades of lock units 320 are arranged in correspondence with on the first output shaft 31, four or eight grades of lock units
420 and 57 grades of lock units 410 are arranged in correspondence with on the second output shaft 41, and reversing-gear synchronizer 510 is arranged in correspondence with the 3rd
On output shaft 51.Lock unit is for engaging the driven gear on three output shafts to export power with corresponding output shaft.Tool
Body ground, a third gear lock unit 310 is arranged between first speed driven gear 32 and third gear driven gear 33, and for driven by one grade
Gear 32 or third gear driven gear 33 are connected to described first output shaft 31.Two or six grades of lock units 320 are arranged on two grades of driven tooth
Between wheel 35 and six grades of driven gears 34, and for two grades of driven gears 35 or six grades of driven gears 34 are connected to described first
Output shaft 31.Four or eight grades of lock units 420 are arranged between fourth gear driven gear 45 and eight grades of driven gears 44, and for by fourth gear
Driven gear 45 or eight grades of driven gears 44 are connected to described second output shaft 41.Five or seven grades of lock units 410 be arranged on five grades from
Between moving gear 43 and seven grades of driven gears 42, and for five grades of driven gears 43 or seven grades of driven gears 42 are connected to described
Second output shaft 41.Reversing-gear synchronizer 510 is arranged between parking ratchet wheel 52 and reverse gear driven gear 53, and for by reverse gear from
Moving gear 53 is connected to the 3rd output shaft 51.In other embodiments, the position of reversing-gear synchronizer 510 can be driven along with reverse gear
The change in location of gear 53 and change.
According to one embodiment of present invention, speed change gear can also include that the first main deceleration output gear 36, second is main
Deceleration output gear 46 and the 3rd main deceleration output gear 54.First main deceleration output gear 36 is arranged on the first output shaft 31
And can rotate along with the rotation of the first output shaft 31, it is preferably provided at one end of the first output shaft 31, and it can be by dynamic
Power exports to differential assembly 60.The most above-mentioned final gear assembly includes first main deceleration output gear the 36, second main deceleration
Output gear 46 and the 3rd main deceleration output gear 54.
The present invention is provided with three odd number shelves driving gears on the first power shaft 11, and Qi Zhongsan, five grades of driving gears are altogether
With.Second power shaft 21 is provided with two even gear driving gears, wherein two, fourth gear driving gear share, six, eight grades of masters
Moving gear shares, and reverse driving gear uses two fourth gear driving gears, can realize eight drive shifts and the power of a reverse gear
Transmission.This double each gear layout of clutch speed variator of eight speed is simple, and cost is relatively low, it is possible on existing seven speed speed change gears
Simply transform and can realize.
In order to set up reverse gear torque ratio, first clutch 71 remains off, and second clutch 72 is coupled to be sent out
The power that motivation transmission comes passes to the second power shaft 21 by second clutch 72.The rotation of primary input axle sequentially passes through second
Clutch 22, two grades of driven gears 35 of the 72, second power shaft 21, two fourth gear driving gear, reverse gear driven gear 53, reverse gear synchronize
Device 510 assembly, the 3rd main deceleration output gear 54 of output shaft the 51, the 3rd, and pass to main reduction driven gear 61, through differential mechanism
Power is passed by assembly 60.
In order to set up one grade of torque ratio, second clutch 72 remains off, and first clutch 71 is coupled to be sent out
The power that motivation transmission comes passes to the first power shaft 11 by first clutch 71, and a third gear lock unit 310 is driven with one grade
Gear 32 engages.The rotation of primary input axle sequentially passes through 11, one grade of driving gear 13, of first clutch the 71, first power shaft
Shelves driven gear 32, third gear lock unit the 310, first output shaft the 31, first main deceleration output gear 36, and pass to main deceleration
Driven gear 61, passes power through differential assembly 60.
In order to set up two grades of torque ratios, first clutch 71 remains off, and second clutch 72 is coupled to be sent out
It is driven with two grades that the power that motivation transmission comes passes to 21,26 grades of lock units 320 of the second power shaft by second clutch 72
Gear 35 engages.The rotation of primary input axle sequentially pass through second clutch the 72, second power shaft 21, two fourth gear driving gear 22,
Two grades of driven gears, 35,26 grades of lock unit 320, first output shafts the 31, first main deceleration output gear 36, and pass to main subtracting
Speed driven gear 61, passes power through differential assembly 60.
In order to set up third gear torque ratio, second clutch 72 remains off, and first clutch 71 is coupled to be sent out
The power that motivation transmission comes passes to the first power shaft 11 by first clutch 71, and a third gear lock unit 310 is driven with third gear
Gear 33 engages.The rotation of primary input axle sequentially pass through 11,35 grades of driving gears 14 of first clutch the 71, first power shaft,
Third gear driven gear 33, one third gear lock unit the 310, first output shaft the 31, first main deceleration output gear 36, and pass to main subtracting
Speed driven gear 61, passes power through differential assembly 60.
In order to set up fourth gear torque ratio, first clutch 71 remains off, and second clutch 72 is coupled to be sent out
It is driven with fourth gear that the power that motivation transmission comes passes to 21,48 grades of lock units 420 of the second power shaft by second clutch 72
Gear 45 engages.The rotation of primary input axle sequentially pass through second clutch the 72, second power shaft 21, two fourth gear driving gear 22,
Fourth gear driven gear 45,48 grades of lock unit 420, second output shafts the 41, second main deceleration output gear 46, and pass to main subtracting
Speed driven gear 61, passes power through differential assembly 60.
In order to set up five grades of torque ratios, second clutch 72 remains off, and first clutch 71 is coupled to be sent out
It is driven with five grades that the power that motivation transmission comes passes to 11,57 grades of lock units 410 of the first power shaft by first clutch 71
Gear 43 engages.The rotation of primary input axle sequentially pass through 11,35 grades of driving gears 14 of first clutch the 71, first power shaft,
Five grades of driven gears, 43,57 grades of lock unit 410, second output shafts the 41, second main deceleration output gear 46, and pass to main subtracting
Speed driven gear 61, passes power through differential assembly 60.
In order to set up six grades of torque ratios, first clutch 71 remains off, and second clutch 72 is coupled to be sent out
It is driven with six grades that the power that motivation transmission comes passes to 21,26 grades of lock units 320 of the second power shaft by second clutch 72
Gear 34 engages.The rotation of primary input axle sequentially pass through 21,68 grades of driving gears 23 of second clutch the 72, second power shaft,
Six grades of driven gears, 34,26 grades of lock unit 320, first output shafts the 31, first main deceleration output gear 36, and pass to main subtracting
Speed driven gear 61, passes power through differential assembly 60.
In order to set up seven grades of torque ratios, second clutch 72 remains off, and first clutch 71 is coupled to be sent out
It is driven with seven grades that the power that motivation transmission comes passes to 11,57 grades of lock units 410 of the first power shaft by first clutch 71
Gear 42 engages.The rotation of primary input axle sequentially passes through 11, seven grades of driving gears 12, seven of first clutch the 71, first power shaft
Shelves driven gear 42,57 grades of lock unit 410, second output shafts the 41, second main deceleration output gear 46, and pass to main deceleration
Driven gear 61, passes power through differential assembly 60.
In order to set up eight grades of torque ratios, first clutch 71 remains off, and second clutch 72 is coupled to be sent out
It is driven with eight grades that the power that motivation transmission comes passes to 21,48 grades of lock units 420 of the second power shaft by second clutch 72
Gear 44 engages.The rotation of primary input axle sequentially pass through 21,68 grades of driving gears 23 of second clutch the 72, second power shaft,
Eight grades of driven gears, 44,48 grades of lock unit 420, second output shafts the 41, second main deceleration output gear 46, and pass to main subtracting
Speed driven gear 61, passes power through differential assembly 60.
In order to set up parking torque ratio, first clutch 71 and second clutch 72 all remain off, halting mechanism
Engage with parking ratchet wheel 52.Braking torque sequentially passes through the 3rd main deceleration output gear 54 of output shaft the 51, the 3rd, and passes to main
Reduction driven gear 61, is kept to zero through differential assembly 60, stationary vehicle, it is achieved parking function by car speed.
Second embodiment according to the present invention, the difference between itself and first embodiment is: three odd number shelves masters
Moving gear is one grade of driving gear 13, third speed drive gear and five or seven grades of driving gears respectively.It is understandable that five or seven grades of masters
Moving gear is the shared gear of five grades and seven grades.Specifically, these three odd number shelves driving gears are arranged on as follows
At one power shaft 11, with reference to the set-up mode of Fig. 1, according to the order from the close-by examples to those far off of the distance between second power shaft 21 one end
For: five or seven grades of driving gears, one grade of driving gear 13 and third speed drive gear.
Second embodiment according to the present invention, be arranged on four driven gears at the first output shaft 31 include one grade from
Moving gear 35, five grades of driven gears of 32, two grades of driven gears and six grades of driven gears 34.Specifically, these four driven gears are pressed
Be arranged at the first output shaft 31 according to following manner, see Fig. 1, according to the distance between double clutch 70 draw near suitable
Sequence is: 32, five grades of driven gears of first speed driven gear, six grades of driven gears 34 and two grades of driven gears 35.
Thus, first speed driven gear 32 engages with one grade of driving gear 13 thus constitutes one grade of gear pair, two grades of driven tooth
Wheel 35 engages with two fourth gear driving gears 22 thus to constitute intermediate gear secondary, and five grades of driven gears and five or seven grades of driving gears engage
Thus constituting five grades of gear pairs, six grades of driven gears 34 engage with six or eight grades of driving gears 23 thus constitute six step tooth wheel set.
It is arranged on four driven gears at the second output shaft 41 and includes third gear driven gear, fourth gear driven gear 45, seven
Shelves driven gear and eight grades of driven gears 44.Specifically, these four driven gears are arranged on the second output shaft as follows
At 41, seeing Fig. 1, the order drawn near according to the distance between double clutch 70 is: third gear driven gear, seven grades driven
Gear, eight grades of driven gears 44 and fourth gear driven gear 45.
Thus, third gear driven gear engages with third speed drive gear thus constitutes third gear pair, fourth gear driven gear 45
Engage with two fourth gear driving gears 22 thus to constitute fourth gear secondary, seven grades of driven gears engage with five or seven grades of driving gears thus
Constituting seven grades of gear pairs, eight grades of driven gears 44 engage with six or eight grades of driving gears 23 thus constitute eight grades of gear pairs.Due to two
Shelves gear pair and fourth gear pair can share two fourth gear driving gears 22, five grades of gear pairs and seven grades of gear pairs and can share five
Seven grades of driving gears, six step tooth wheel set and eight grades of gear pairs can share six or eight grades of driving gears 23, can reduce by three masters altogether
Moving gear so that speed change gear compact conformation, assembly length shortens, it is simple to the layout of vehicle engine assembly.Owing to ensureing in fact
Under existing desired speed ratio premise, the driving gear on power shaft uses shared gear train to greatest extent, reduces number of teeth quantity,
Making its structure compacter, the length of assembly is shorter.
Second embodiment according to the present invention, five lock units be respectively a Five-gear synchronizer, two or six grades of lock units, four
Eight grades of lock units, Radix Notoginseng shelves lock unit and reversing-gear synchronizer.One Five-gear synchronizer and two or six grades of lock units are arranged in correspondence with
On one output shaft, four or eight grades of lock units and Radix Notoginseng shelves lock unit are arranged in correspondence with on the second output shaft, and reversing-gear synchronizer is corresponding
Be arranged on the 3rd output shaft.Lock unit is for engaging the driven gear on three output shafts with defeated with corresponding output shaft
Go out power.Specifically, a Five-gear synchronizer is arranged between first speed driven gear and five grades of driven gears, and for by one grade from
Moving gear or five grades of driven gears are connected to described first output shaft.Two or six grades of lock units are arranged on two grades of driven gears and six grades
Between driven gear, and for two grades of driven gears or six grades of driven gears are connected to described first output shaft.Four or eight grades same
Step device is arranged between fourth gear driven gear and eight grades of driven gears, and for fourth gear driven gear or eight grades of driven gears are connected
Receive described second output shaft.Radix Notoginseng shelves lock unit is arranged between third gear driven gear and seven grades of driven gears, and for inciting somebody to action
Third gear driven gear or seven grades of driven gears are connected to described second output shaft.Reversing-gear synchronizer is arranged on parking ratchet wheel and reverse gear
Between driven gear, and for reverse gear driven gear is connected to the 3rd output shaft.In other embodiments, reversing-gear synchronizer
Position can change along with the change in location of reverse gear driven gear.It should be appreciated that by lock unit and associated teeth wheels
Various combination, it is possible to realize concrete advance or reverse speed ratio, still belong to the scope of protection of the invention.
So far, although those skilled in the art will appreciate that the multiple of the most detailed present invention of illustrate and describing show
Example embodiment, but, without departing from the spirit and scope of the present invention, still can be direct according to present disclosure
Determine or derive other variations or modifications of many meeting the principle of the invention.Therefore, the scope of the present invention is it is understood that and recognize
It is set to and covers other variations or modifications all these.
Claims (10)
1. an eight speed double-clutch speed change gear, including:
For receiving the primary input axle of motor torque；
First input equipment, including the first power shaft for rotating coaxially with described primary input axle be arranged on described first defeated
Enter three odd number shelves driving gears at axle；
Secondary input device, including for rotating coaxially with described primary input axle and at least partially around described first power shaft
The second power shaft and be arranged on two even gear driving gears at described second power shaft；
Double clutch, described double clutch includes for the torque of primary input axle optionally passes to described first power shaft
First clutch and second clutch with described second power shaft；
First output device, including the first parallel with described primary input axle and arranged apart with described primary input between centers output shaft
With four driven gears being arranged at the first output shaft, four driven gears at described first output shaft all can selectivity
Be connected to described first output shaft with common rotation；
Second output device, including the second parallel with described primary input axle and arranged apart with described primary input between centers output shaft
With four driven gears being arranged at the second output shaft, four driven gears at described second output shaft all can selectivity
Be connected to described second output shaft with common rotation；
3rd output device, including the 3rd parallel with described primary input axle and arranged apart with described primary input between centers output shaft
With the reverse gear driven gear being arranged at the 3rd output shaft, described reverse gear driven gear can be used to selectively connect to the described 3rd
Output shaft is with common rotation；
Multiple lock units, the plurality of lock unit for by least one in all driven gears and described first output shaft,
At least one in second output shaft and the 3rd output shaft is selectively connected；
Wherein, one in described three odd number shelves driving gears is the shared driving gear engaged with two driven gears, institute
The each of which stating two even gear driving gears is the shared driving gear engaged with two driven gears, described first output
One in four driven gears at axle is engaged with described reverse gear driven gear as reverse gear intermediate idler.
Eight speed double-clutch speed change gears the most according to claim 1, wherein, three odd numbers at described first power shaft
Shelves driving gear is respectively one grade of driving gear, three or five grades of driving gears and seven grades of driving gears, described three or five grades of driving gears
For third gear and the shared driving gear of five grades；
Four driven gears at described first output shaft are respectively first speed driven gear, two grades of driven gears, third gear driven tooth
Wheel and six grades of driven gears；
Four driven gears at described second output shaft are respectively fourth gear driven gear, five grades of driven gears, seven grades of driven tooth
Wheel and eight grades of driven gears.
Eight speed double-clutch speed change gears the most according to claim 2, wherein, described three at described first power shaft
Odd number shelves driving gear is three or five grades of driving gears, one grade of driving tooth relative to described double clutch order from the close-by examples to those far off successively
Wheel and seven grades of driving gears；
Wherein, described three or five grades of driving gears engage with described third gear driven gear and described five grades of driven gears respectively；
Described one grade of driving gear engages with described first speed driven gear；
Described seven grades of driving gears engage with described seven grades of driven gears.
4., according to eight speed double-clutch speed change gears described in Claims 2 or 3, wherein, the plurality of lock unit includes one or three
Shelves lock unit, two or six grades of lock units, four or eight grades of lock units, five or seven grades of lock units and reversing-gear synchronizer；
A described third gear lock unit is arranged at described first output shaft, for by first speed driven gear and third gear driven tooth polling
Selecting property it is connected to described first output shaft；
Described two or six grades of lock units are arranged at described first output shaft, for by two grades of driven gears and six grades of driven tooth pollings
Selecting property it is connected to described first output shaft；
Described four or eight grades of lock units are arranged at described second output shaft, for by fourth gear driven gear and eight grades of driven tooth pollings
Selecting property it is connected to described second output shaft；
Described five or seven grades of lock units are arranged at described second output shaft, for by five grades of driven gears and seven grades of driven tooth pollings
Selecting property it is connected to described second output shaft；
Described reversing-gear synchronizer is arranged at described 3rd output shaft, described for being used to selectively connect to by reverse gear driven gear
3rd output shaft.
Eight speed double-clutch speed change gears the most according to claim 1, wherein, three odd numbers at described first power shaft
Shelves driving gear is respectively one grade of driving gear, third speed drive gear and five or seven grades of driving gears, described five or seven grades of driving gears
It it is the shared gear of five grades and seven grades；
Four driven gears at described first output shaft are respectively first speed driven gear, two grades of driven gears, five grades of driven tooth
Wheel and six grades of driven gears；
Four driven gears at described second output shaft are respectively third gear driven gear, fourth gear driven gear, seven grades of driven tooth
Wheel and eight grades of driven gears.
Eight speed double-clutch speed change gears the most according to claim 5, wherein, described three at described first power shaft
Odd number shelves driving gear is five or seven grades of driving gears, one grade of driving tooth relative to described double clutch order from the close-by examples to those far off successively
Wheel and third speed drive gear；
Wherein, described five or seven grades of driving gears engage with described five grades of driven gears and described seven grades of driven gears respectively；
Described one grade of driving gear engages with described first speed driven gear；
Described third speed drive gear engages with described third gear driven gear.
7., according to eight speed double-clutch speed change gears described in claim 5 or 6, wherein, the plurality of lock unit includes the First Five-Year Plan
Shelves lock unit, two or six grades of lock units, Radix Notoginseng shelves lock unit, four or eight grades of lock units and reversing-gear synchronizer；
A described Five-gear synchronizer is arranged at described first output shaft, for by first speed driven gear and five grades of driven tooth pollings
Selecting property it is connected to described first output shaft；
Described two or six grades of lock units are arranged at described first output shaft, for by two grades of driven gears and six grades of driven tooth pollings
Selecting property it is connected to described first output shaft；
Described Radix Notoginseng shelves lock unit is arranged at described second output shaft, for by third gear driven gear and seven grades of driven tooth pollings
Selecting property it is connected to described second output shaft；
Described four or eight grades of lock units are arranged at described second output shaft, for by fourth gear driven gear and eight grades of driven tooth pollings
Selecting property it is connected to described second output shaft；
Described reversing-gear synchronizer is arranged at described 3rd output shaft, described for being used to selectively connect to by reverse gear driven gear
3rd output shaft.
8. according to eight speed double-clutch speed change gears according to any one of claim 1-7, wherein, at described second power shaft
Two even gear driving gears be respectively two fourth gear driving gears and six or eight grades of driving gears, described two fourth gear driving gears are
Two grades and the shared gear of fourth gear, described six or eight grades of driving gears are the shared gear of six grades and eight grades；
Described two fourth gear driving gears engage with described two grades of driven gears and described fourth gear driven gear respectively；
Described six or eight grades of driving gears engage with described six grades of driven gears and described eight grades of driven gears respectively.
9. according to eight speed double-clutch speed change gears according to any one of claim 1-8, wherein, described reverse gear driven gear
Engage with described two grades of driven gears, so that described two grades of driven gears are as described reverse gear intermediate idler；
Alternatively, described reverse gear driven gear engages with described first speed driven gear, so that described first speed driven gear conduct
Described reverse gear intermediate idler.
Eight speed double-clutch speed change gears the most according to claim 9, wherein, are additionally provided with at described 3rd output shaft
Parking ratchet wheel；
Described first output device also includes being arranged on the main deceleration output gear of first at the first output shaft；
Described second output device also includes being arranged on the main deceleration output gear of second at the second output shaft；
Described 3rd output device also includes the 3rd main deceleration output gear being arranged at the 3rd output shaft；
Described device also includes slow down output main with described first main deceleration output gear, the second main deceleration output gear and the 3rd
The main reduction driven gear that gear connects jointly.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610887296.2A CN106321748A (en) | 2016-10-11 | 2016-10-11 | Eight-speed double clutch speed change device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610887296.2A CN106321748A (en) | 2016-10-11 | 2016-10-11 | Eight-speed double clutch speed change device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106321748A true CN106321748A (en) | 2017-01-11 |
Family
ID=57821329
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610887296.2A Pending CN106321748A (en) | 2016-10-11 | 2016-10-11 | Eight-speed double clutch speed change device |
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| Country | Link |
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| CN (1) | CN106321748A (en) |
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| CN110701261A (en) * | 2019-10-08 | 2020-01-17 | 宁波上中下自动变速器有限公司 | Automatic transmission and vehicle |
| CN111853170A (en) * | 2019-04-25 | 2020-10-30 | 广州汽车集团股份有限公司 | Eight-speed double-clutch type automatic transmission and vehicle |
| CN113492667A (en) * | 2020-03-20 | 2021-10-12 | 广州汽车集团股份有限公司 | Hybrid power driving system and vehicle |
| CN113606297A (en) * | 2021-08-11 | 2021-11-05 | 宁波上中下自动变速器有限公司 | Double-clutch automatic transmission and vehicle |
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| CN111853170A (en) * | 2019-04-25 | 2020-10-30 | 广州汽车集团股份有限公司 | Eight-speed double-clutch type automatic transmission and vehicle |
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| CN113606297A (en) * | 2021-08-11 | 2021-11-05 | 宁波上中下自动变速器有限公司 | Double-clutch automatic transmission and vehicle |
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