CN103470699B - Double-clutch-transmdriven driven mechanism - Google Patents
Double-clutch-transmdriven driven mechanism Download PDFInfo
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- CN103470699B CN103470699B CN201310321351.8A CN201310321351A CN103470699B CN 103470699 B CN103470699 B CN 103470699B CN 201310321351 A CN201310321351 A CN 201310321351A CN 103470699 B CN103470699 B CN 103470699B
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- clutch
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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
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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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
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention discloses a kind of Double-clutch-transmdriven driven mechanism, including first, second double-row planetary gear, at least one uses CR CR formula gear shifts in two planet circular systems, including front and rear two planet row, in preceding planet row, front ring gear is connected with rear planet carrier by synchronizer or clutch, and preceding planet carrier is connected with rear gear ring and be connected as power output with output shaft, power is input into by preceding sun gear, or is input on rear sun gear or rear planet carrier by synchronizer or clutch.The present invention is by using CR CR formulas gear shifts and Ravigneaux formula gear shift, the combination of Simpson gear shift, and coordinate two clutches, multiple synchronizers to use, realize the shift property of dual-clutch transmission, and transmission dimensions can be reduced, while gear shift ride comfort is improved.
Description
Technical field
The present invention relates to automotive transmission technical field, a kind of Double-clutch-transmdriven driven mechanism is concretely related to.
Background technology
Automotive transmission transmission mechanism presses train pattern difference used, there is axis interconnection system speed changer (parallel shaft transmission)
With two kinds of axis rotary speed gear (planetary transmission).Can be divided into single clutch speed changer and double by the quantity of clutch
Clutch speed changer.The actuating unit of the double-clutch speed changer of application is parallel shaft transmission at present, and power transmission is divided into two
Bar route, one is odd number shelves transfer route, and two is even gear transfer route, two articles of power transmission lines respectively by first, the
Two clutches connect first, second input shaft, then by the travelling gear on driven shaft corresponding with two input shafts that power is defeated
Go out, double-clutch speed changer is controlled by the coordination of two clutches and each synchronizer is controlled, and can realize not cutting off the feelings of power
Transmission ratio under condition, so as to shorten shift time.But parallel-axis type double-clutch speed changer must use single reversing shaft
And back gear.When using an output shaft, speed changer axial dimension is big；During using two output shafts, speed changer radial ruler
It is very little big, take up room big, it is unfavorable for the structure layout design of automobile.The double-clutch speed changer drive shift of application is at most used at present
7 grades, most widely used is six grades, and total gearratio is small, and when gear is set, one grade of gearratio is also smaller, engine displacement compared with
Automobile is shaken phenomenon when starting easily occurs in small automobile, and engine speed is higher during high speed, is changed greatly with speed per hour ratio, this
Engine speed is changed greatly during sample gear shift, makes the dynamic property of automobile, economical all less desirable, and ride comfort is poor.
The content of the invention
The technical problem to be solved in the present invention is to provide a kind of Double-clutch-transmdriven driven mechanism by brand new,
Structure is more compact, reduces the axially and radially size of speed changer, while forward can be with more, to overcome prior art
It is not enough.
In order to solve the above technical problems, the technical solution adopted by the present invention is：A kind of Double-clutch-transmdriven driven mechanism, bag
Include the first clutch and corresponding first input shaft, the second clutch and corresponding second input shaft, multiple synchronizers, output shaft, institute
First and second input shaft sheathed setting is stated, also including first, second double-row planetary gear, intermeshing first gear and second
Gear and the 3rd gear and the 4th gear；At least one double-row planetary gear is adopted in first, second double-row planetary gear
With CR-CR formula gear shifts, including front and rear two planet row, in preceding planet row, front ring gear is with rear planet carrier by synchronous
Device or clutch are connected, and preceding planet carrier is connected with rear gear ring and be connected with output shaft as power output, and power passes through
Preceding sun gear input, or be input on rear sun gear or rear planet carrier by synchronizer or clutch.
The preceding sun gear of the first double-row planetary gear is connected with the second input shaft, the planet carrier of preceding planet row and rear planet row
Gear ring and first gear connection；Rear sun gear is connected with the first outer shaft, and rear planet carrier is connected with the first middle axle sleeve.
The preceding sun gear of second double-row planetary gear is connected with the second jackshaft and the 4th gear, the second double planet
The planet carrier of the preceding planet row of train is connected with the gear ring and second gear of rear planet row, and rear sun gear and the second outer shaft connect
Connect, rear planet carrier is connected with the second middle axle sleeve.
First often engages synchronizer is located between the first double-row planetary gear front ring gear and rear planet carrier, and the second synchronizer sets
Put between the rear planet carrier and the first outer shaft of the first double-row planetary gear, the 3rd synchronizer is arranged on the second input shaft and
Between first middle axle sleeve of one double-row planetary gear, second often engagement synchronizer be located at the second double-row planetary gear front ring gear with
Afterwards between planet carrier, the 5th synchronizer is arranged between the rear planet carrier of the second double-row planetary gear and the second outer shaft, and the 6th
Synchronizer is arranged between the 7th synchronizer of the second double-row planetary gear and the second outer shaft, and the 7th synchronizer is arranged on the 4th
Between gear and the second middle axle sleeve of the second double-row planetary gear.
First, second clutch is arranged on the first double-row planetary gear right side, and output shaft is arranged on the second double planetary gear
Fasten and set between not coaxial line, the second input shaft and the rear sun gear of the first planet circular system with first, second clutch
Six grades of synchronizers.
First, second clutch is arranged on the first double-row planetary gear right side, and output shaft is arranged on the first double planetary gear
Fasten and with first, second clutch on the same axis.
First double-row planetary gear uses CR-CR formula gear shifts, and the second double-row planetary gear is tieed up using drawing
Na formula gear shift.
First double-row planetary gear uses Simpson gear shift, and the second double-row planetary gear uses CR-
CR formula gear shifts.
The first gear or second gear are engaged with main reducing gear driven gear, main reducing gear driven gear connection differential
Device.
Compared with prior art, the present invention has advantages below：The present invention is the base in existing dual-clutch transmission
On plinth, by using CR-CR formulas gear shift and Ravigneaux formula gear shift, Simpson gear shift
Combination, and coordinate two clutches, multiple synchronizers to use, make it can both reach with few gear logarithm realization more multi-speed
Than the purpose of gear, the power shift performance of dual-clutch transmission can be realized again, and can reduce the axial direction and footpath of speed changer
To size, controlled the size of speed changer, vehicle structure layout designs are more flexible, while can reduce being produced into
This.TR increases simultaneously, increases total gearratio, and when gear is set, one grade of gearratio makes to start also than larger
Automobile is shaken phenomenon when the less automobile of machine discharge capacity is not easy to occur starting, and engine speed is relatively low during high speed, because speed compares
Change is smaller, and engine speed change is smaller during such gear shift, makes the dynamic property of automobile, economical all more satisfactory, while changing
Shelves ride comfort is improved.
Brief description of the drawings
Fig. 1 is the power drive mechanism schematic diagram of double-clutch speed changer first embodiment of the present invention；
Fig. 2 is the power drive mechanism schematic diagram of second embodiment of the invention；
Fig. 3 is the power drive mechanism schematic diagram of third embodiment of the invention；
Fig. 4 is the power drive mechanism schematic diagram of fourth embodiment of the invention；
Fig. 5 is the power drive mechanism schematic diagram of fifth embodiment of the invention；
Fig. 6 is the power drive mechanism schematic diagram of sixth embodiment of the invention；
Fig. 7 is the power drive mechanism schematic diagram of seventh embodiment of the invention；
Fig. 8 is the power drive mechanism schematic diagram of eighth embodiment of the invention；
Fig. 9 is the structural representation of the output form change of double-clutch speed changer of the present invention.
Specific embodiment
First double-row planetary gear of the invention and the second double-row planetary gear can using CR-CR formulas gear shift,
Simpson gear shift or Ravigneaux formula gear shift, but the first double-row planetary gear and the second double planetary gear
It is that at least one double-row planetary gear uses CR-CR formula gear shifts.Various transmission schemes can be obtained by combination.
Below, with reference to Figure of description and specific embodiment, technical scheme is further described.
First, second double-row planetary gear is the embodiment of CR-CR formula gear shifts：
First embodiment（Eight grades）
Referring to Fig. 1, double clutch of the invention includes that double clutch components 1 (including the first clutch 2 and the second clutch 3, are distinguished
Correspondence two clutches the first input shaft 4, the second input shaft 5, the first double-row planetary gear 100, the second double-row planetary gear 101,
Output shaft 130 and multiple synchronizers.First double-row planetary gear and the second double-row planetary gear are with up-down structure arrangement
CR-CR formula gear shifts, the first double-row planetary gear includes front and rear two planet rows, and preceding planet row is the first planet row X1,
Planet row is the second planet row X2 afterwards, and the second double-row planetary gear includes that third planet arranges X3（Before second double-row planetary gear
Planet row）And fourth planet row X4（The rear planet row of the second double-row planetary gear）.
The preceding sun gear 114 of the first double-row planetary gear is connected with the second input shaft 5, the first planet row X1（Preceding planet row）
The planet row X2 of planet carrier 111 and second（Planet row afterwards）Gear ring 116 and first gear 181 connect.Rear sun gear 119 and
One outer shaft 123 is connected.Planet carrier 120 is connected with the first middle axle sleeve 122 afterwards.
The preceding sun gear 134 of the second double-row planetary gear is connected with the second jackshaft 143 and the 4th gear 184, the third line
Star arranges X3（Preceding planet row）Planet carrier 131 and fourth planet arrange X4（Planet row afterwards）Gear ring 136 and second gear 182 connect
Connect.Rear sun gear 139 is connected with the second outer shaft 145.Planet carrier 140 is connected with the second middle axle sleeve 144 afterwards.
The other end of first input shaft 4 is connected with the 3rd gear 183, and the 3rd gear 183 is engaged with the 4th gear 184, and first
Gear 181 is engaged with second gear 182, and second gear 182 is connected with output shaft 8, and output shaft 8 is with dual clutch pack 1 same
Side.
First often engages synchronizer 115 is located between the front ring gear 112 of the first double-row planetary gear 100 and rear planet carrier 120,
Second synchronizer（2nd, fourth gear synchronizer 117）It is arranged on the outer shaft of rear planet carrier 120 and first of the first double-row planetary gear 100
Between set 123.3rd synchronizer（6th, eight grades of synchronizers 121）It is arranged on the second input shaft 5 and the first double-row planetary gear 100
The first middle axle sleeve 122 between.
Second often engages synchronizer 135 is located between the front ring gear 132 of the second double-row planetary gear 101 and rear planet carrier 140,
5th synchronizer（First, third gear synchronizer 137）It is arranged on the outer shaft of rear planet carrier 140 and second of the second double-row planetary gear 101
Between set 145.6th synchronizer（Reversing-gear synchronizer 141）Be arranged on the 7th synchronizer 142 of the second double-row planetary gear 101 with
Between second outer shaft 145.7th synchronizer（5th, seven grades of synchronizers 142）It is arranged on the 4th gear 184 and the second double planet
Between second middle axle sleeve 144 of train 101.
The double-clutch speed changer of the present embodiment can realize eight fast drive shifts and a fast reverse gear.First double-row planetary gear 100
Realize that two, four, six, eight gears are controlled.Second double-row planetary gear 101 realizes one, three, five, seven grades and reverse gear manipulation.
It is as follows in the action of each gear synchronizer and clutch：
During neutral state, as shown in figure 1, first often engagement synchronizer 115 by the first double-row planetary gear front ring gear 112 with
Planet carrier 120 links together afterwards, and second often engages synchronizer 135 by the second double-row planetary gear front ring gear 132 and rear planet
Frame 140 links together.2nd, fourth gear synchronizer 117 and, third gear synchronizer 137 is in an intermediate position.6th, eight grades of synchronizers
121 and five, seven grades of synchronizers 142 and reversing-gear synchronizer 141 be in not engagement state on right side.
One grade：First, third gear synchronizer 137 is moved to left, by the rear planet carrier 140 and second in the second double-row planetary gear 101
Often the engagement double-row planetary gear front ring gear 132 of synchronizer 135 and second is connected and not rotated, such second double-row planetary gear 101
Form restriction relation.First clutch 2 is engaged simultaneously.Power passes to the first input shaft 4, the 3rd gear through first clutch 2
183, the 4th gear 184, then through the second double-row planetary gear 101 to output shaft.Now second clutch 3 is in released state,
Remaining synchronizer is in position during neutral state.
Two grades：2nd, fourth gear synchronizer 117 is moved to left, and the rear planet carrier 120, first in the first double-row planetary gear 101 is normal
Engagement synchronizer 115 and front ring gear 112 are connected and not rotated, and such first double-row planetary gear 100 forms restriction relation.First from
Clutch 2 is separated, while second clutch 3 is engaged, power passes to the second input shaft 5 through first clutch 2, through the first double row
Star wheel series 100, first gear 181, second gear 182, then exported by output shaft 8.
Third gear：First, third gear synchronizer 137 is moved to right, and the second outer shaft 145 is connected, so that also by the second double planetary gear
The rear sun gear 139 of system connects motionless.Second clutch 3 is separated, and first clutch 2 is engaged, and realizes that third gear power is transmitted.
Fourth gear：2nd, fourth gear synchronizer 117 is moved to right, and the first outer shaft 123 is connected, so that also by the first double planetary gear
The rear sun gear 119 of system connects motionless.First clutch 2 is separated, and second clutch 3 is engaged, and realizes that fourth gear power is transmitted.Power
The second input shaft 5 is passed to through second clutch 2, through the first double-row planetary gear 181, first gear 161, second gear 162,
Exported by output shaft 8 again.
Five grades：5th, seven grades of synchronizers 142 are moved to left, and the 4th gear 184 is attached with the second middle axle sleeve 144.Second
Clutch 3 is separated, and first clutch 2 is engaged, and realizes five grades of power transmission.
Six grades：6th, eight grades of synchronizers 121 are moved to left, and the second input shaft 5 is attached with the first middle axle sleeve 122.First
Clutch 2 is separated, and second clutch 3 is engaged, and realizes six grades of shelves power transmission.It is defeated that power passes to second through second clutch 2
Enter axle 5, through the first double-row planetary gear 181, first gear 161, second gear 162, then exported by output shaft 8.
Seven grades：5th, seven grades of synchronizers 142 are moved to left, and the 4th gear 184 are attached with the second middle axle sleeve 144, second
Often engagement synchronizer 135 is moved to right, and the second double-row planetary gear front ring gear 132 is disengaged with rear planet carrier 140 and is separated, while
First, third gear synchronizer 137 is moved to right, by the second outer shaft 145, so as to also connect the rear sun gear 139 of the second double-row planetary gear
Connect motionless.Second clutch 3 is separated, and first clutch 2 is engaged, and realizes seven grades of power transmission.
Eight grades：6th, eight grades of synchronizers 121 are moved to left, and the second input shaft 5 is attached with the first middle axle sleeve 122.First
Often engagement synchronizer 115 is moved to right, and the first double-row planetary gear front ring gear 112 is disengaged with rear planet carrier 120 and is separated, while
2nd, fourth gear synchronizer 117 is moved to right, by the first outer shaft 123, so as to also connect the rear sun gear 139 of the second double-row planetary gear
Connect motionless.First clutch 2 is separated, and second clutch 3 is engaged, and realizes eight grades of shelves power transmission.
Reverse gear：Reversing-gear synchronizer 141 is moved to left, and the second outer shaft 145 is connected with five, seven grades of synchronizers 142, and one, third gear
Synchronizer 137 is moved to left, and the rear planet carrier 140 in the second double-row planetary gear 101 is connected and is not rotated.Second clutch 3 is separated,
First clutch 2 is engaged, and realizes that reverse gear power is transmitted.
Double-clutch speed changer in the invention can realize various transforming gear patterns：
Order shift mode：
Order upshifts, and is raised to as a example by two grades by one grade, and before shifting commands send, speed changer is in a gear working condition.It is accurate
It is standby to implement to need in advance to move to left the front ring gear 112 in the first double-row planetary gear 100 two, fourth gear synchronizer 117 before shifting gears
Connection is not rotated, and now first clutch 2 and second clutch 3 are still respectively at engagement and released state.Work as control system
Shifting commands are sent when one grade is raised to two grades, all synchronizer hold modes are motionless, and first clutch 2 is progressively separated, while
Second clutch 3 is progressively engaged, until first clutch 2 is kept completely separate, second clutch 3 is fully engaged, at the same simultaneously control one,
Third gear synchronizer 137 returns to centre position, makes the second double-row planetary gear front ring gear 132 unfettered, remaining and one grade and two
The unrelated synchronizer of shelves is also failure to actuate.The order upshift and order downshift of other gears also deduce in the same way.
Jump shift mode：
The jump that odd gear changes to even gear rises downshift, and such as one grade is raised to fourth gear or five grades drop to two grades, even number
The jump that gear changes to odd gear rises downshift, and such as two upshifts drop to five to five grades or eight grades, and its gear changing mode rises with order
The control method of shelves is the same, can be deduced with same method.
Odd gear changes to the jump upshift of odd gear, so that one grade rises third gear as an example, before shifting commands send, and speed changer
In a gear working condition.Prepare implement gearshift before, first clutch 2 is separated, one, third gear synchronizer 137 briefly return to interposition
Put, then move to right the rear sun gear 139 of the second double-row planetary gear is connected motionless.First clutch 2 is rejoined, and completes one grade and rises
The control of third gear.In the process, second clutch 3 is constantly in released state, and remaining is unrelated with one grade and third gear synchronous
Device is also failure to actuate.Odd gear change to odd gear jump downshift and even gear change to even gear jump rise downshift with
The jump upshift control method that odd gear changes to odd gear is the same, can be deduced with same method.
The setting of each gear gearratio can be by each planet rowValue（Equal to planet row the gear ring number of teeth with
The ratio between sun gear number of teeth）, first gear 181 and second gear 182 gearratioAnd the 3rd gear 183 and the 4th gear 184
GearratioTo set.For example setting the first double-row planetary gear includes the first planet row X1 and the second planet row X2, and second is double
Planet circular system includes that third planet arranges X3's and fourth planet row X4Value is respectively 2.4,3.1,3.4,2.6,1,1.19, then obtain each gear gearratio, the working condition than level and synchronizer shown in table 1.From
Numerically see, the gearratio of each gear, it is more appropriate than level rationally, and total gear ratio reaches 6.93, obtains good speed change bit
Property.
The eight speed transmission of table 1 each gear gearratio, the working condition than level and synchronizer
Note："○" represents clutch engagement or synchronizer action
Second embodiment（Seven grades）
Referring to Fig. 2, on the basis of first embodiment, double clutch components 1 are arranged on the first double-row planetary gear 100 right
Side, output shaft 8 is arranged in the second double-row planetary gear 101 with double clutch components 1 in not coaxial line and not in the same side, is cancelled
6th, eight grades of middle axle sleeves 122 of synchronizer 121 and first, and in the second input shaft 5 and the rear sun gear 119 of the first planet circular system
Between set six grades of synchronizers 124.Set according to gear gearratio need it is appropriate change first gear 181 and second gear 182,
The gearratio of the 3rd gear 183 and the 4th gear 184, and each planet rowValue.Such first double-row planetary gear 100
Two, four, six grades are realized, the second double-row planetary gear 101 realizes one, three, five, seven and reverse gear.
3rd embodiment（Six grades）
Referring to Fig. 3, on the basis of second embodiment, by output shaft 8 be arranged in the first double-row planetary gear 100 with it is double
, in same axis in not homonymy, often 141 and five, seven grades of engagement synchronizer 135 and reversing-gear synchronizer are same to cancel second for clutch component 1
Step device 142, and six grades of synchronizers 146 are set between the gear 184 of rear sun gear 139 and the 4th of the second planet circular system.
Recover the first normal engagement synchronizer 115 in first embodiment in one double-row planetary gear 100.Passed to better meet gear
It is dynamic to be needed than setting, can suitably change the biography of first gear 181 and second gear 182, the 3rd gear 183 and the 4th gear 184
Dynamic ratio, and each planet rowValue.First double-row planetary gear 100 realizes one, three, five and reverse gear, the second double planet
Train 101 realizes two, four, six grades.
From above embodiment, output shaft 8 can change with the position relationship of double clutch components 1, when output shaft 8 sets
Not homonymy and the same side can be placed on double clutch components 1 when putting in the second double-row planetary gear 101, be exported in not homonymy
Axle 8 both can be with double clutch components 1 in same axis or in not coaxial line, and at the same side, output shaft 8 can only be with double clutch groups
Part 1 is in not coaxial line.Can only be in not homonymy when output shaft 8 is arranged in the first double-row planetary gear 100, but same output shaft
8 can with double clutch components 1 in same axis also in not coaxial line.Odd number shelves or even gear may be provided at the first double planetary gear
Being 100 also can be in the second double-row planetary gear 101.The first double-row planetary gear and second double is obtained from there through permutation and combination
Planet circular system is 18 kinds of transmission schemes of CR-CR formulas gear shift, referring to table 2.
The double-row planetary gear of table 2 first and the second double-row planetary gear are CR-CR formula gear shift transmission schemes
First, second double-row planetary gear is used by CR-CR formulas gear shift and Ravigneaux formula gear shift
The embodiment of combination：
Fourth embodiment（Eight grades）
Referring to Fig. 4, on the basis of first embodiment, the second double-row planetary gear is used into Ravigneaux formula change set
Structure.Second double-row planetary gear 101 includes that third planet arranges X3 and fourth planet row X4, small sun gear 233 and short planetary gear
232 engagement simultaneously be connected with the second middle axle sleeve 243, short planetary gear 232 is engaged with planetary gear long 231, big sun gear with also with length
Planetary gear 231 is engaged and is connected with the second outer shaft 242, and short planetary gear 232 and planetary gear long 231 are installed in planet carrier 235
On, planet carrier 235 is connected with the second jackshaft 241, and gear ring 234 is connected with second gear and output shaft 8, and one, third gear synchronizer
237 install planet carriers 235 and between, reversing-gear synchronizer 238 be arranged on second often engagement the outer shaft of synchronizer 239 and second
Between 242, second often engages synchronizer 239 is arranged between five, seven grades of middle axle sleeves 243 of synchronizer 240 and second, and five, seven
Shelves synchronizer 240 is arranged between the second jackshaft 241 and the 4th gear 184.
The setting of each gear gearratio can be by each planet rowValue（Equal to planet row the gear ring number of teeth with
The ratio between sun gear number of teeth）, first gear 181 and second gear 182 transmission when the 3rd gear 183 is passed with the 4th gear 184
It is dynamic to compare to set.
The shift mode of the embodiment is consistent with first embodiment, and the first double-row planetary gear realizes two, four, six, eight grades,
First double-row planetary gear realizes one, three, five, seven and reverse gear.
5th embodiment（Seven grades）
Referring to Fig. 5, on the basis of fourth embodiment, double clutch components 1 are placed on the first double-row planetary gear 100
Opposite side, such output shaft 8 with double clutch components 1 respectively in not homonymy and not on the same axis, cancels the second double planet
The second jackshaft 241, reversing-gear synchronizer 238, second in train 101 often engage 239 and five, seven grades of synchronizers of synchronizer
240, six grades of synchronizers 245 are set between the second outer shaft 242 and the 4th gear 284, and in the first double-row planetary gear 100
Increase reversing-gear synchronizer 125.Being set according to gear gearratio needs appropriate change first gear 181 and second gear the 182, the 3rd
The transmission of gear 183 and the 4th gear 184 when each planet rowValue.First double-row planetary gear 100 realizes one, three,
5th, seven and reverse gear, the second double-row planetary gear 101 realizes two, four, six grades.
Sixth embodiment（Six grades）
Referring to Fig. 6, on the basis of the 5th embodiment, by the first double-row planetary gear and the position of the second double-row planetary gear
Put exchange, output shaft 8 is placed on on the same axis of the first double-row planetary gear, and in not homonymy, cancels reversing-gear synchronizer 124
And five, seven grades of synchronizers 121, increase Five-gear synchronizer 124.Being set according to gear gearratio needs appropriate change first gear
181 are driven when each planet row with second gear 182, the 3rd gear 183 and the 4th gear 184Value.First is double
Planet circular system 100 realizes two, four, six grades, and the second double-row planetary gear 101 realizes one, three, five and reverse gear.
From fourth, fifth, six embodiments, in combination with first, second and third embodiment situation, output shaft 8 and double clutch groups
The position relationship alterable of part 1, can be placed on when output shaft 8 is arranged in the second double-row planetary gear with double clutch components 1
Not homonymy and the same side, in not homonymy output shaft 8 both can with double clutch components 1 in same axis or in not coaxial line,
Output shaft 8 can only be with double clutch components 1 in not coaxial line during the same side.When output shaft 8 is arranged in the first double-row planetary gear
When can only in not homonymy, but same output shaft 8 can with double clutch components 1 in same axis also in not coaxial line.Odd number shelves or
Even gear may be provided at the first double-row planetary gear also can in the second double-row planetary gear, meanwhile, CR-CR formula gear shifts
And Ravigneaux gear shift both could be arranged to odd number shelves and may be alternatively provided as even gear, and it is double to be both placed on first
Planet circular system may also placed in the second double-row planetary gear.36 kinds of transmission schemes are obtained from there through permutation and combination, referring to table 3.
Table 3 combines transmission scheme by CR-CR formulas gear shift and Ravigneaux gear shift
First, second double-row planetary gear is used by CR-CR formulas gear shift and Simpson gear shift
The embodiment of combination：
7th embodiment（Seven grades）
Referring to Fig. 7, on the basis of embodiment one, the first double-row planetary gear is used into Simpson change set
Structure.First double-row planetary gear 100 includes the first planet row X1 and the second planet row X2, in the first double-row planetary gear 100
Front ring gear 312 is connected with the second input shaft 5, preceding sun gear 314 and rear sun gear 319 and first in the first double-row planetary gear
Axle sleeve 321 is connected, and the empty set of the first axle sleeve 321 is on the first input shaft 4.Preceding planet carrier 313, rear gear ring 315 and first gear 181
Link together, six grades of synchronizers 317 are arranged between rear gear ring 315 and rear planet carrier 318, two, fourth gear synchronizer 320 is located at
Afterwards between the axle sleeve 321 of planet carrier 318 and first.Being set according to gear gearratio needs appropriate change first gear 181 and second
The transmission of gear 182, the 3rd gear 183 and the 4th gear 184 when each planet rowValue.First double-row planetary gear
100 realize that two, four, six gears are controlled.Second double-row planetary gear 101 realizes one, three, five, seven grades and reverse gear manipulation.
8th embodiment（Six grades）
On the basis of the 7th embodiment, output shaft 8 be placed on on the same axis of the first double-row planetary gear, and not
Homonymy, cancels the second middle axle sleeve 144, reversing-gear synchronizer 141 and five or seven grades of synchronizers 142, increases Five-gear synchronizer 147.Root
Being set according to gear gearratio needs appropriate change first gear 181 and second gear 182, the 3rd gear 183 and the 4th gear 184
Transmission when each planet rowValue.First double-row planetary gear 100 realizes that two, four, six gears are controlled.Second double row
Star wheel series 101 realize one, three, five grades and reverse gear manipulation.
From the seven, the eight embodiments, in combination with the situation of first, second, third and fourth, five, six embodiments, output shaft 8 with
The position relationship alterable of double clutch components 1, can be with double clutch groups when output shaft 8 is arranged in the second double-row planetary gear
Part 1 is placed on not homonymy and the same side, and in not homonymy, output shaft 8 both can be with double clutch components 1 in same axis or in difference
Axis, at the same side, output shaft 8 can only be with double clutch components 1 in not coaxial line.When output shaft 8 is arranged on the first double planet
Wheel when fastening can only in not homonymy, but same output shaft 8 can with double clutch components 1 in same axis also in not coaxial line.Very
Several grades or even gear may be provided at the first double-row planetary gear also can in the second double-row planetary gear, meanwhile, CR-CR formulas gear becomes
Fast mechanism and Simpson gear shift both could be arranged to odd number shelves and may be alternatively provided as even gear, and can both be placed on
First double-row planetary gear may also placed in the second double-row planetary gear, but in seven speed transmissions, only CR-CR formulas
Gear shift can just be set to odd number shelves, both one, three, five, seven grades.18 kinds of transmission sides are obtained from there through permutation and combination
Case, referring to table 4.
Table 4 combines transmission scheme by CR-CR formulas gear shift and Simpson gear shift
In all transmission modes, change and each planet rowThe transmission when the 3rd of value, first gear and second gear
Gear and the 4th gear ratio, while adjusting the action of speed shift executive component, then gear sets and can suitably change, eight
Gear gearbox change turns to a planet row and realizes one, three, five, six, and another planet row realizes two, four, seven, eight grades, seven grades of changes
Fast device change turns to a planet row and realizes one, three, five, six, and another planet row realizes two, four, seven grades, and reverse gear typically sets and one
Shelves are on same planet row.By taking seven speed transmissions as an example, referring to Fig. 2, if first double-row planetary gear the first planet row X1 and
Second planet row X2, the second double-row planetary gear includes that third planet arranges X3's and fourth planet row X4Value is respectively
3.2,2.1,3.5,3.5, if the gearratio of first gear 181 and second gear 182And the 3rd gear
183 and the gearratio of the 4th gear 184Respectively0.8,1.25, then obtain each different gear gearratios, than level
And the working condition of synchronizer, referring to table 5, such first double-row planetary gear 100 realizes two, four, seven grades, the second double planet
Train 101 realizes one, three, five, six.Numerically, the gearratio of each gear, it is more appropriate than level rationally, and total gear ratio reaches
To 7.03, preferable speed change ratio characteristic is obtained.
The seven speed transmissions of table 5 each gear gearratios, the working condition than level and synchronizer
In addition, in all transmission modes, output form of double clutch components with output shaft in the same side can suitably change,
Referring to Fig. 9, reduce first gear 181 and the diameter of second gear 182, two gears are directly engaged with main reducing gear driven gear 190,
And power is externally exported by differential mechanism 191.
Claims (6)
1. a kind of Double-clutch-transmdriven driven mechanism, including the first clutch and corresponding first input shaft, the second clutch and correspondence
The second input shaft, multiple synchronizers, output shaft, first input shaft and the second input shaft sheathed setting also include
First double-row planetary gear, the second double-row planetary gear, intermeshing first gear and second gear, the intermeshing 3rd
Gear and the 4th gear；It is characterized in that：In first double-row planetary gear and second double-row planetary gear at least
One double-row planetary gear uses CR-CR formula gear shifts, including front and rear two planet row, in preceding planet row, front ring gear
It is connected by synchronizer or clutch with rear planet carrier, preceding planet carrier is connected with rear gear ring and be connected conduct with output shaft
Power output, power is input into by preceding sun gear, or is input to rear sun gear or rear planet carrier by synchronizer or clutch
On；The preceding sun gear of the first double-row planetary gear is connected with the second input shaft, the tooth of the planet carrier of preceding planet row and rear planet row
Circle and first gear connection；Rear sun gear is connected with the first outer shaft, and rear planet carrier is connected with the first middle axle sleeve；First often nibbles
Close synchronizer to be located between the first double-row planetary gear front ring gear and rear planet carrier, the second synchronizer is arranged on the first double planet
Between the rear planet carrier and the first outer shaft of train, the 3rd synchronizer is arranged on the second input shaft and the first double-row planetary gear
Between first middle axle sleeve, second often engages synchronizer is located between the second double-row planetary gear front ring gear and rear planet carrier, the
Five synchronizers are arranged between the rear planet carrier of the second double-row planetary gear and the second outer shaft, and the 6th synchronizer is arranged on second
Between 7th synchronizer of double-row planetary gear and the second outer shaft, the 7th synchronizer is arranged on the 4th gear and the second double row
Between second middle axle sleeve of star wheel series.
2. Double-clutch-transmdriven driven mechanism according to claim 1, it is characterised in that：First, second clutch is set
On the right side of the first double-row planetary gear, output shaft is arranged in the second double-row planetary gear and with first, second clutch not
Six grades of synchronizers are set between the rear sun gear of coaxial line, the second input shaft and the first planet circular system.
3. Double-clutch-transmdriven driven mechanism according to claim 1, it is characterised in that：First, second clutch is set
On the right side of the first double-row planetary gear, output shaft is arranged in the first double-row planetary gear and with first, second clutch same
On one axis.
4. Double-clutch-transmdriven driven mechanism according to claim 1, it is characterised in that：First double-row planetary gear
Using CR-CR formula gear shifts, the second double-row planetary gear uses Ravigneaux formula gear shift.
5. Double-clutch-transmdriven driven mechanism according to claim 1, it is characterised in that：First double-row planetary gear
Using Simpson gear shift, the second double-row planetary gear uses CR-CR formula gear shifts.
6. Double-clutch-transmdriven driven mechanism according to claim 1, it is characterised in that：The first gear or second gear
Engaged with main reducing gear driven gear, main reducing gear driven gear connected with differential.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201310321351.8A CN103470699B (en) | 2013-07-27 | 2013-07-27 | Double-clutch-transmdriven driven mechanism |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310321351.8A CN103470699B (en) | 2013-07-27 | 2013-07-27 | Double-clutch-transmdriven driven mechanism |
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| CN103470699A CN103470699A (en) | 2013-12-25 |
| CN103470699B true CN103470699B (en) | 2017-06-27 |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106068402B (en) * | 2014-02-17 | 2018-07-20 | 工程中心斯太尔有限两合公司 | The double-clutch speed changer that can be shifted gears under full load |
| US9638292B1 (en) * | 2015-10-27 | 2017-05-02 | Schaeffler Technologies AG & Co. KG | CVT differential |
| CN109654180B (en) * | 2019-02-15 | 2023-05-26 | 汤久望 | Planetary and fixed shaft compound speed change mechanism |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5445042A (en) * | 1993-10-21 | 1995-08-29 | General Motors Corporation | Transmission and control with hydraulically actuated synchronizers |
| CN201841948U (en) * | 2010-09-28 | 2011-05-25 | 安徽江淮汽车股份有限公司 | Dual clutch transmission driver |
| CN102352913A (en) * | 2011-09-30 | 2012-02-15 | 长城汽车股份有限公司 | Multi-gear vertical dual clutch transmission |
| CN102797812A (en) * | 2012-08-23 | 2012-11-28 | 赵良红 | Double-clutch transmission device |
| CN203453399U (en) * | 2013-07-27 | 2014-02-26 | 赵良红 | Double-clutch speed changer transmission mechanism |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6837823B2 (en) * | 2002-12-19 | 2005-01-04 | General Motors Corporation | Six-speed dual-clutch transmissions having four planetary gear sets and two brakes |
-
2013
- 2013-07-27 CN CN201310321351.8A patent/CN103470699B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5445042A (en) * | 1993-10-21 | 1995-08-29 | General Motors Corporation | Transmission and control with hydraulically actuated synchronizers |
| CN201841948U (en) * | 2010-09-28 | 2011-05-25 | 安徽江淮汽车股份有限公司 | Dual clutch transmission driver |
| CN102352913A (en) * | 2011-09-30 | 2012-02-15 | 长城汽车股份有限公司 | Multi-gear vertical dual clutch transmission |
| CN102797812A (en) * | 2012-08-23 | 2012-11-28 | 赵良红 | Double-clutch transmission device |
| CN203453399U (en) * | 2013-07-27 | 2014-02-26 | 赵良红 | Double-clutch speed changer transmission mechanism |
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| CN103470699A (en) | 2013-12-25 |
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