CN202484216U - Six-speed double-clutch type automatic gearbox - Google Patents
Six-speed double-clutch type automatic gearbox Download PDFInfo
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- CN202484216U CN202484216U CN 201220067838 CN201220067838U CN202484216U CN 202484216 U CN202484216 U CN 202484216U CN 201220067838 CN201220067838 CN 201220067838 CN 201220067838 U CN201220067838 U CN 201220067838U CN 202484216 U CN202484216 U CN 202484216U
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—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 characterised by the disposition of the gears
- F16H3/093—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 characterised by the disposition of the gears with two or more countershafts
- F16H2003/0931—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 characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
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Abstract
The utility model provides a six-speed double-clutch type automatic gearbox, belongs to the field of mechanical technology, and solves the technical problems of the conventional six-speed double-clutch type automatic gearbox that the loading capacity of the whole car is reduced due to an excessively long reverse gear shaft, and the like. The six-speed double-clutch type automatic gearbox comprises a clutch I, a clutch II, a differential mechanism and five shafts arranged in parallel, wherein the five shafts include an input shaft I, an input shaft II, an output shaft I, an output shaft II and a reverse gear shaft; a main reduction gear I and a main reduction gear II are engaged with a main reduction driven gear of the differential mechanism; a reverse gear input gear and a reverse gear output gear are sequentially arranged on the reverse gear shaft; a reverse gear driven gear is also arranged on the output shaft II; and the reverse gear input gear is engaged with two reverse gear driving gears, and the reverse gear driven gear is positioned between a six-gear reversing synchronizer and the main reduction gears. The six-speed double-clutch type automatic gearbox has the advantages that the reverse gear shaft is relatively short, and therefore, the loading capacity of the whole car is improved.
Description
Technical field
The utility model belongs to field of mechanical technique, relates to a kind of speed changer, particularly a kind of six speed double-clutch formula automatic transmission.
Background technique
Supply with more and more severelyer along with domestic petroleum, emission regulation demands is more and more stricter, and non-professional driver constantly rises simultaneously, market demand high efficiency, high-comfort, automatic transmission cheaply.The employed automatic transmission of automobile is broadly divided into three types at present: one type of hydraulic automatic speed variator AT that is made up of fluid torque converter, planetary gears and electrohydraulic control system (Automatic Transmission); One type of electric control mechanical type automatic speed variator AMT (Automated Manual Transmission) that forms by conventional fixed shaft type gearbox and dry clutch and corresponding electrohydraulic control system; Another kind of is electrodeless automatic transmission CVT (Continuously Variable Transminssion).
The AT stable starting is quickened rapidly, even, soft, has become the leading products of world today's vehicular automatic transmission, but complex structure, make difficulty, cost is high, its efficient is lower simultaneously, oil consumption is higher, the atrophy day by day of the present market share.Though the AMT price is low than AT,, produce shift impact and gearshift noise because there is power interruption in shift process.Though CVT can realize real stepless change, need very high pressure between belt and the belt wheel and step up power, so big by the loss that hydraulic-pressure pump produced, transmission efficiency is low, and belt cost cost is high simultaneously, and maintenance expenses is big; Bearing torque has narrow limitation etc.
Double-clutch automatic transmission DCT (Double Clutch Transmission) has realized the power gear shifting of shift process, promptly interrupts power at shift process, has overcome the deficiency of AMT, has solved the shortcoming of AMT shift impact.The good advantages of shift quality such as AT, CVT have been kept.This makes vehicle in shift process; The power of motor can be delivered to wheel all the time, and gearshift has rapidly steadily not only guaranteed the acceleration of vehicle; And, also improved the travelling comfort of vehicle operating greatly because vehicle no longer produces the abrupt deceleration situation that causes owing to gearshift.
Two clutch gearboxes have combined the advantage of manual transmission and automatic transmission case, do not use torque-converters, then adopt two cover clutches, through the mutual alternation of two cover clutches, arrive the effect of crack gearshift continuously.Two groups of clutches are controlled odd number retaining and even number retaining respectively, are exactly particularly before gearshift, and self shifter mechanism is in advance with next shift gear engagement; After obtaining shifting commands, self shifter mechanism sends instruction to motor rapidly, and engine speed raises; This moment, previous meshed gears combined rapidly; First group of clutch decontroled fully simultaneously, accomplishes once to rise the retaining action, and the action of back by that analogy.
DCT can make the length of whole gearbox shorten owing to adopt the double output shaft structure simultaneously, and is compact more; On the basis of MT length, can arrange more gear; Gear number whole adds makes that respectively to keep off speed ratio more reasonable, can obtain better power character and economic index, reduces oil consumption.Be to promote the technology of DCT, reduce oil consumption, make DCT can be contained on the wider vehicle, this just requires the axial dimension of DCT and radial dimension littler, so that can adaptive different vehicle.The disclosed double-clutch automatic transmission of Chinese patent document [application publication number CN101713448A] for example; Comprise first input shaft and second input shaft and first clutch and second clutch, first input shaft is provided with first output shaft, second output shaft and the reverse gear shaft parallel with second input shaft with first input shaft with second input shaft side; Be equipped with several even number retaining driving gears that rotate synchronously with first input shaft on first input shaft; Second input shaft protrudes from and is equipped with the odd number retaining driving gear and the driving gear that reverses gear that several and second input shaft rotate synchronously on the position of first input shaft: be provided with first final gear, several driven gears on first output shaft successively: be provided with second final gear and several driven gears and the driven gear that reverses gear on second output shaft successively: main deceleration driven gear and two differential gears are installed on the differential mechanism, main deceleration driven gear respectively with first output shaft on first final gear and the engagement of second final gear on second output shaft.Because the driving gear that will reverse gear is arranged on second output shaft, has increased the length of reverse gear shaft, has increased manufacture cost, the long clutch complete machine that also causes of the length of reverse gear shaft becomes big in addition, makes the lift-launch property reduction of car load.
Summary of the invention
The purpose of the utility model is to have the problems referred to above to existing technology, has proposed a kind of compact structure, six short speed double-clutch formula automatic transmission of reverse gear shaft.
The purpose of the utility model can realize through following technical proposal: a kind of six speed double-clutch formula automatic transmission; Comprise clutch one, clutch two, differential mechanism and five axles that laterally arrange: input shaft one, input shaft two, output shaft one, output shaft two and reverse gear shaft; One end of described input shaft two is connected with clutch two, and the other end of input shaft two is provided with four or six retaining driving gears and two retaining driving gears successively; Described input shaft one coaxial being located in the input shaft two, an end of input shaft one is connected with clutch one, and the other end of input shaft one passes described input shaft two and is provided with a retaining driving gear successively and three or five retaining driving gears; Be provided with a retaining driven gear, one or three retaining synchronizers, three retaining driven gears, four retaining driven gears, two or four retaining synchronizers, two retaining driven gear and final gears one on the described output shaft one successively; Be provided with five retaining synchronizers, five retaining driven gears, six retaining driven gears, six reverse gear synchronizer and final gears two on the described output shaft two successively; Final gear one often meshes with the main deceleration driven gear of final gear two with differential mechanism; It is characterized in that; Be provided with reverse gear the input gear and the output gear that reverses gear on the described reverse gear shaft successively; Also be provided with the driven gear that reverses gear on the described output shaft two, the described input gear that reverses gear can be meshed with two driving gears that reverse gear, and the described driven gear that reverses gear reverses gear between synchronizer and the final gear six.
These six speed double-clutch formula automatic transmission also comprise the self shifter mechanism by ECU control; When vehicle was in the Parking state, clutch one was in separated state with clutch two, not transferring power; When vehicle was started to walk with a retaining, self shifter mechanism engaged one or three retaining synchronizers and a retaining driven gear, and gear switches to a retaining, and clutch one combines, and clutch two keeps off state, and vehicle begins to keep off operation with one; Vehicle is in when operation retaining, because this moment, clutch two was in separated state, and transferring power not; When vehicle quickens, when reaching the shifting points near two retainings, self shifter mechanism can change to two retainings in advance with gear; Be about to two or four retaining synchronizers and engage with two retaining driven gears, when hanging two retainings, clutch one separates; Clutch two engages, and whole shift process finishes, and vehicle changes to two retainings; After vehicle got into two retaining operations, ECU can be according to the current running state of relevant sensor signals perception vehicle, and then judges that vehicle is about to get into the gear of operation; If vehicle quickens; Then next gear is three retainings, if vehicle deceleration, then next gear is a retaining; And a retaining and three retainings are by clutch one control; Because clutch one is in separated state, transferring power not is so can instruct self shifter mechanism to change to the gear that is about to the work of getting in advance; When vehicle operating reaches shifting points; Clutch two separation that only need will work, clutch one engages simultaneously, and vehicle just can be hung and corresponding gear; During reversing, gear is hung into the gear that reverses gear, and clutch one separates, and clutch two engages; Power passes to input shaft two through clutch two, passes to the input gear that reverses gear through two retaining driving gears on the input shaft two, passes to reverse gear shaft; Pass to the output gear that reverses gear, pass to the driven gear that reverses gear, through six reverse gear synchronizer pass to output two; Pass to main deceleration driven gear through final gear two, send out power, because reverse gear shaft is short through differential mechanism; Reduced high request, also reduced the size of speed changer simultaneously accordingly, provided cost savings the technology intensity of reverse gear shaft.
In the six speed double-clutch formula automatic transmission of the above, a described retaining driving gear can be meshed with a retaining driven gear, and described three or five retaining driving gears can be meshed with three retaining driven gears and five retaining driven gears.During one retaining, a retaining driving gear is meshed with a retaining driven gear, through one or three retaining synchronizers transmission of power is arrived differential mechanism; In 3 whens retaining, three or five retaining driving gears and three retaining driven gears engagements arrive differential mechanism through one or three retaining synchronizers with transmission of power; In 5 whens retaining, three or five retaining driving gears and five retaining driven gears engagements arrive differential mechanism through five retaining synchronizers with transmission of power.
In the six speed double-clutch formula automatic transmission of the above, described four or six the retaining driving gears can with six the retaining driven gears and four the retaining driven gears be meshed, described two reverse gear driving gear can with two the retaining driven gears be meshed.In 2 whens retaining, two driving gears that reverse gear are meshed with two retaining driven gears, through two or four retaining synchronizers transmission of power are arrived differential mechanism; During four retainings, four or six retaining driving gears are meshed with four retaining driven gears, through two or four retaining synchronizers transmission of power are arrived differential mechanism; In 6 whens retaining, four or six retaining driving gears are meshed with six retaining driven gears, through six synchronizers that reverse gear transmission of power are arrived differential mechanism.
In the six speed double-clutch formula automatic transmission of the above; The described input gear that reverses gear is connected with reverse gear output gear and reverse gear shaft; Described final gear one is connected with output shaft one; Final gear two is connected with output shaft two, and a described retaining driving gear and three or five retaining driving gears are connected with input shaft one, and four or six keep off reverse gear driving gear and input shaft two of driving gears and two is connected.
In the six speed double-clutch formula automatic transmission of the above; Described two retaining driven gears, four retaining driven gears, three retaining driven gears and a retaining driven gear are enclosed within on the output shaft one through the bearing sky respectively, and described six retaining driven gears, five retaining driven gears and the driven gear that reverses gear are enclosed within on the output shaft two through the bearing sky.For driven gear is rotated meshing in advance with corresponding driving gear but do not drive output shaft; Driven gear is enclosed within on the output shaft through the bearing sky; When the driven gear of corresponding gear needs outputting power, realize the output of outputting axial power by corresponding synchronous device and being connected of driven gear.
Compared with prior art, these six speed double-clutch formula automatic transmission have following advantage:
1, the driven gear that reverses gear is arranged between six retaining driven gears and the final gears one, reverses gear to import gear and can be meshed with two driving gears that reverse gear, and makes reverse gear shaft shorter; Simultaneously, the shared driving gear of three or five retainings, the public gear of four or six retainings makes compact structure, it is shorter that corresponding speed changer can design, and improved its car load and carried property, greatly reduces manufacture cost.
2, the switching through double clutch and shift to an earlier date change to corresponding gear, make power failure-free when gearshift to make driving more comfortable steadily.
Description of drawings
Fig. 1 is the structural representation of these six speed double-clutch formula automatic transmission.
Among the figure, 1a, final gear one; 1b, final gear two; 2, reverse gear shaft; 3, the input gear that reverses gear; 4, the output gear that reverses gear; 5, the driven gear that reverses gear; 6, six synchronizers that reverse gear; 7, six retaining driven gears; 8, four or six retaining driving gears; 9, five retaining driven gears; 10, three or five retaining driving gears; 11, five retaining synchronizers; 12, output shaft two; 13, input shaft two; 14, a retaining driving gear; 15, input shaft one; 16, a retaining driven gear; 17, output shaft one; 18, one or three retaining synchronizers; 19, three retaining driven gears; 20, four retaining driven gears; 21, two or four retaining synchronizers; 22, two retaining driving gears; 23, two retaining driven gears; 24a, differential mechanism; 24b, main deceleration driven gear; 25a, clutch one; 25b, clutch two.
Embodiment
Below be the specific embodiment of the utility model and combine accompanying drawing, the technological scheme of the utility model is done further to describe, but the utility model is not limited to these embodiments.
As shown in Figure 1; A kind of six speed double-clutch formula automatic transmission; Comprise clutch one 25a, clutch two 25b, differential mechanism 24a and five axles that laterally arrange: input shaft 1, input shaft 2 13, output shaft 1, output shaft 2 12 and reverse gear shaft 2, these six speed double-clutch formula automatic transmission also comprise the self shifter mechanism by ECU control.
One end of input shaft 2 13 is connected with clutch two 25b, and the other end of input shaft 2 13 is provided with four or six retaining driving gears 8 and two retaining driving gears 22 successively; Input shaft one 15 coaxial being located in the input shaft 2 13, an end of input shaft 1 is connected with clutch one 25a, and the other end of input shaft 1 passes described input shaft 2 13 and is provided with a retaining driving gear 14 successively and three or five retaining driving gears 10;
Be provided with retaining driven gear 16,1 retaining synchronizers 18, three retaining driven gears 19, four retaining driven gears, 20,24 retaining synchronizers 21, two retaining driven gear 23 and final gear one 1a on the output shaft 1 successively; Two retaining driven gears 23, four keep off driven gears 20, three retaining driven gears 19 and a retaining driven gear 16 and are enclosed within on the output shaft 1 through the bearing sky respectively;
On output shaft 2 12, be provided with five retaining synchronizers 11, five retaining driven gears 9, six retaining driven gears 7, six reverse gear synchronizer 6 and final gear two 1b successively; Six retaining driven gears 7, five keep off driven gears 9 and the driven gear 5 that reverses gear is enclosed within on the output shaft 2 12 through the bearing sky; Reverse gear driving gear and input shaft 2 13 of four or six retaining driving gears 8 and two is connected.
Final gear one 1a and output shaft 1 are connected, and final gear two 1b and output shaft 2 12 are connected, and the main deceleration driven gear 24b of final gear one 1a and final gear two 1b and differential mechanism 24a often meshes.
Be provided with reverse gear the input gear 3 and the output gear 4 that reverses gear on the reverse gear shaft 2 successively; Also be provided with the driven gear 5 that reverses gear on the output shaft 2 12; The input gear 3 that reverses gear is connected with reverse gear shaft 2 with the output gear 4 that reverses gear; The input gear 3 that reverses gear can be meshed with two driving gears that reverse gear, and the driven gear 5 that reverses gear reverses gear between synchronizer 6 and the final gear six.
One retaining driving gear 14 can be meshed with a retaining driven gear 16, and three or five retaining driving gears 10 can be meshed with three retaining driven gears 19 and five retaining driven gears 9; Four or six retaining driving gears 8 can be meshed with six retaining driven gears 7 and four retaining driven gears 20, and two driving gears that reverse gear can keep off driven gears 23 and be meshed with two.
Concrete transmission process is following: when vehicle was in the Parking state, clutch one 25a and clutch two 25b were in separated state, not transferring power; When vehicle was started to walk with a retaining, self shifter mechanism engaged one or three retaining synchronizers 18 and a retaining driven gear 16, and gear switches to a retaining, and clutch one 25a combines, and clutch two 25b keep off state, and vehicle begins to move with a retaining.
One retaining power transmission line: power passes to input shaft 1 through clutch one 25a; Pass to a retaining driven gear 16 through a retaining driving gear 14 on the input shaft 2 13; Pass to one of output through one or three retaining synchronizers 18; Pass to main deceleration driven gear 24b through final gear one 1a, 24a goes out transmission of power through differential mechanism.
Vehicle is in when operation retaining, because this moment, clutch two 25b were in separated state, and transferring power not; When vehicle quickens, when reaching the shifting points near two retainings, self shifter mechanism can change to two retainings in advance with gear; Be about to two or four retaining synchronizers 21 and engage with two retaining driven gears 23, when hanging two retainings, clutch one 25a separates; Clutch two 25b engage, and whole shift process finishes, and vehicle changes to two retainings.
Two retaining power transmission lines: power passes to input shaft 2 13 through clutch two 25b; Pass to two retaining driven gears 23 through two retaining driving gears 22 on the input shaft 1; Pass to one of output through two or four retaining synchronizers 21; Pass to main deceleration driven gear 24b through final gear two 1b, 24a goes out transmission of power through differential mechanism.
After vehicle got into two retaining operations, ECU can be according to the current running state of relevant sensor signals perception vehicle, and then judges that vehicle is about to get into the gear of operation; If vehicle quickens; Then next gear is three retainings, if vehicle deceleration, then next gear is a retaining; And a retaining and three retainings are controlled by clutch one 25a; Because clutch one 25a is in separated state, transferring power not is so can instruct self shifter mechanism to change to the gear that is about to the work of getting in advance; When vehicle operating reaches shifting points; Only need clutch two 25b that will work to separate, clutch one 25a engages simultaneously, and vehicle just can be hung and corresponding gear; The handoff procedure of other gear that advances also is like this.
Three retaining power transmission lines: power passes to input shaft 1 through clutch one 25a; Pass to three retaining driven gears 19 through three or five retaining driving gears 10 on the input shaft 1; Pass to one of output through one or three retaining synchronizers 18; Pass to main deceleration driven gear 24b through final gear one 1a, 24a goes out transmission of power through differential mechanism.
Four retaining power transmission lines: power passes to input shaft 1 through clutch two 25b; Pass to four retaining driven gears 20 through four or six retaining driving gears 8 on the input shaft 1; Pass to one of output through two or four retaining synchronizers 21; Pass to main deceleration driven gear 24b through final gear one 1a, 24a goes out transmission of power through differential mechanism.
Five retaining power transmission lines: power passes to input shaft 1 through clutch one 25a; Pass to five retaining driven gears 9 through three or five retaining driving gears 10 on the input shaft 1; Pass to two of outputs through five retaining synchronizers 11; Pass to main deceleration driven gear 24b through final gear one 1a, 24a goes out transmission of power through differential mechanism.
Six retaining power transmission lines: power passes to input shaft 2 13 through clutch two 25b; Pass to six retaining driven gears 7 through four or six retaining driving gears 8 on the input shaft 2 13; Through six reverse gear synchronizer 6 pass to output two; Pass to main deceleration driven gear 24b through final gear two 1b, 24a goes out transmission of power through differential mechanism.
The retaining power transmission line reverses gear: power passes to input shaft 2 13 through clutch two 25b; Pass to the input gear 3 that reverses gear through two retaining driving gears 22 on the input shaft 2 13, pass to reverse gear shaft 2, pass to the output gear 4 that reverses gear; Pass to the driven gear 5 that reverses gear; Pass to output shaft 2 12 through six synchronizers 6 that reverse gear, pass to main deceleration driven gear 24b through final gear two 1b, 24a goes out transmission of power through differential mechanism.
Specific embodiment described herein only is that the utility model spirit is illustrated.The utility model person of ordinary skill in the field can make various modifications or replenishes or adopt similar mode to substitute described specific embodiment, but can't depart from the spirit of the utility model or surmount the defined scope of appended claims.
Although this paper has used final gear one 1a morely; Final gear two 1b; Reverse gear shaft 2; Input gear 3 reverses gear; Output gear 4 reverses gear; Driven gear 5 reverses gear; Six synchronizers 6 that reverse gear; Six retaining driven gears 7; Four or six retaining driving gears 8; Five retaining driven gears 9; Three or five retaining driving gears 10; Five retaining synchronizers 11; Output shaft 2 12; Input shaft 2 13; One retaining driving gear 14; Input shaft 1; One retaining driven gear 16; Output shaft 1; One or three retaining synchronizers 18; Three retaining driven gears 19; Four retaining driven gears 20; Two or four retaining synchronizers 21; Two retaining driving gears 22; Two retaining driven gears 23; Main deceleration driven gear 24; Differential mechanism 25; Clutch one 26a; Terms such as clutch two 26b, but do not get rid of the possibility of using other term.Using these terms only is in order to describe and explain the essence of the utility model more easily; It all is contrary with the utility model spirit being construed to any additional restriction to them.
Claims (5)
1. speed double-clutch formula automatic transmission; Comprise clutch one (25a), clutch two (25b), differential mechanism (24a) and five axles that laterally arrange: input shaft one (15), input shaft two (13), output shaft one (17), output shaft two (12) and reverse gear shaft (2); One end of described input shaft two (13) is connected with clutch two (25b), and the other end of input shaft two (13) is provided with four or six retaining driving gears (8) and two retaining driving gears (22) successively; Described input shaft one (15) coaxial being located in the input shaft two (13); One end of input shaft one (15) is connected with clutch one (25a), and the other end of input shaft one (15) passes described input shaft two (13) and is provided with a retaining driving gear (14) successively and three or five retaining driving gears (10); Be provided with a retaining driven gear (16), one or three retaining synchronizers (18), three retaining driven gears (19), four retaining driven gears (20), two or four retaining synchronizers (21), two retaining driven gear (23) and final gears one (1a) on the described output shaft one (17) successively; Be provided with five retaining synchronizers (11), five retaining driven gears (9), six retaining driven gears (7), six reverse gear synchronizer (6) and final gears two (1b) on the described output shaft two (12) successively; Final gear one (1a) and final gear two (1b) and the normal engagement of the main deceleration driven gear (24b) of differential mechanism (24a); It is characterized in that; Be provided with reverse gear input gear (3) and the output gear that reverses gear (4) on the described reverse gear shaft (2) successively; Also be provided with the driven gear that reverses gear (5) on the described output shaft two (12), the described input gear (3) that reverses gear can be meshed with two driving gears that reverse gear, and the described driven gear that reverses gear (5) is positioned at six and reverses gear between synchronizer (6) and the final gear.
2. six speed double-clutch formula automatic transmission according to claim 1; It is characterized in that; A described retaining driving gear (14) can be meshed with a retaining driven gear (16), and described three or five retaining driving gears (10) can be meshed with three retaining driven gears (19) and five retaining driven gears (9).
3. six speed double-clutch formula automatic transmission according to claim 1 and 2; It is characterized in that; Described four or six retaining driving gears (8) can be meshed with six retaining driven gears (7) and four retaining driven gears (20), and described two driving gears that reverse gear can keep off driven gears (23) and be meshed with two.
4. six speed double-clutch formula automatic transmission according to claim 1 and 2; It is characterized in that; The described input gear (3) and the output gear that reverses gear (4) and reverse gear shaft (2) of reversing gear is connected; Described final gear one (1a) and output shaft one (17) are connected; Final gear two (1b) and output shaft two (12) are connected, and a described retaining driving gear (14) is connected with input shaft one (15) with three or five retaining driving gears (10), and four or six keep off reverse gear driving gear and input shaft two (13) of driving gears (8) and two is connected.
5. six speed double-clutch formula automatic transmission according to claim 1 and 2; It is characterized in that; Described two retaining driven gears (23), four retaining driven gears (20), three retaining driven gears (19) and a retaining driven gear (16) are enclosed within on the output shaft one (17) through the bearing sky respectively, and described six retaining driven gears (7), five retaining driven gears (9) and the driven gear that reverses gear (5) are enclosed within on the output shaft two (12) through the bearing sky.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220067838 CN202484216U (en) | 2012-02-28 | 2012-02-28 | Six-speed double-clutch type automatic gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220067838 CN202484216U (en) | 2012-02-28 | 2012-02-28 | Six-speed double-clutch type automatic gearbox |
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| Publication Number | Publication Date |
|---|---|
| CN202484216U true CN202484216U (en) | 2012-10-10 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201220067838 Expired - Fee Related CN202484216U (en) | 2012-02-28 | 2012-02-28 | Six-speed double-clutch type automatic gearbox |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104455238A (en) * | 2014-11-24 | 2015-03-25 | 东风汽车公司 | Three-shaft six-gear manual gearbox |
| CN105736652A (en) * | 2016-04-21 | 2016-07-06 | 中国第一汽车股份有限公司 | Double-clutch type automatic transmission |
| EP3245087A4 (en) * | 2015-01-16 | 2018-01-10 | BYD Company Limited | Transmission unit, power transmission system and vehicle comprising the same |
| CN108180261A (en) * | 2018-02-01 | 2018-06-19 | 淮阴工学院 | A kind of automatic mechanical transmission speed change system |
| CN110360311A (en) * | 2019-08-23 | 2019-10-22 | 河南科技大学 | Tractor hydraulic mechanical type double-clutch automatic gearbox and control method |
| CN113124110A (en) * | 2019-12-31 | 2021-07-16 | 上海汽车集团股份有限公司 | Double-clutch transmission and automobile |
| CN113685497A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
-
2012
- 2012-02-28 CN CN 201220067838 patent/CN202484216U/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104455238A (en) * | 2014-11-24 | 2015-03-25 | 东风汽车公司 | Three-shaft six-gear manual gearbox |
| EP3245087A4 (en) * | 2015-01-16 | 2018-01-10 | BYD Company Limited | Transmission unit, power transmission system and vehicle comprising the same |
| CN105736652A (en) * | 2016-04-21 | 2016-07-06 | 中国第一汽车股份有限公司 | Double-clutch type automatic transmission |
| CN108180261A (en) * | 2018-02-01 | 2018-06-19 | 淮阴工学院 | A kind of automatic mechanical transmission speed change system |
| CN108180261B (en) * | 2018-02-01 | 2023-12-22 | 淮阴工学院 | Speed changing system of mechanical automatic transmission |
| CN110360311A (en) * | 2019-08-23 | 2019-10-22 | 河南科技大学 | Tractor hydraulic mechanical type double-clutch automatic gearbox and control method |
| CN113124110A (en) * | 2019-12-31 | 2021-07-16 | 上海汽车集团股份有限公司 | Double-clutch transmission and automobile |
| CN113685497A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Ten keep off two separation and reunion derailleurs and vehicle |
| CN113685497B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Ten-gear double-clutch transmission and vehicle |
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Granted publication date: 20121010 Termination date: 20140228 |