CN102678839A - Double-clutch transmission used in tractor - Google Patents

Double-clutch transmission used in tractor Download PDF

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Publication number
CN102678839A
CN102678839A CN2011104059439A CN201110405943A CN102678839A CN 102678839 A CN102678839 A CN 102678839A CN 2011104059439 A CN2011104059439 A CN 2011104059439A CN 201110405943 A CN201110405943 A CN 201110405943A CN 102678839 A CN102678839 A CN 102678839A
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China
Prior art keywords
gear
driven gear
shaft
retaining
clutch
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Granted
Application number
CN2011104059439A
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Chinese (zh)
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CN102678839B (en
Inventor
徐立友
周志立
谢金法
彭巧励
曹付义
郗建国
牛毅
李忠利
曹青梅
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Henan University of Science and Technology
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Henan University of Science and Technology
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Priority to CN201110405943.9A priority Critical patent/CN102678839B/en
Publication of CN102678839A publication Critical patent/CN102678839A/en
Application granted granted Critical
Publication of CN102678839B publication Critical patent/CN102678839B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive

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  • Structure Of Transmissions (AREA)

Abstract

The invention relates to a double-clutch transmission used in a tractor. The double-clutch transmission comprises two input shafts, a first intermediate shaft and a second intermediate shaft, wherein the two input shafts are arranged coaxially, the first intermediate shaft and the second intermediate shaft are parallel to the input shafts, an odd number of tap position driving gears and an even number of tap position driving gears are respectively fixed on the two input shafts, and a first driven gear set which is in mesh transmission with the driving gears on the corresponding input shaft is idly sleeved on the first intermediate shaft; and a second driven gear set and a tap position reversing driven gear which are in transmission connection with the driving gears on the corresponding input shaft are idly sleeved on the second intermediate shaft, the first intermediate shaft and the second intermediate shaft are respectively provided with a torque output section which is used for outwards outputting corresponding torque, and the tap position reversing driven gear is in mesh transmission with one driven gear of the first driven gear set. The original tap position reversing idle gear and the original tap position reversing idle gear shaft are eliminated, so that the structure is relatively compact, the quantity of parts is reduced, the manufacturing cost is saved, and the installation difficulty is decreased.

Description

The dual-clutch transmission that uses in a kind of tractor
Technical field
The present invention relates to the speed changer technical field, relate in particular to the dual-clutch transmission that uses in a kind of tractor.
Background technique
The tractor speed changer adopts armstrong's patent gearshift modes such as sliding gear, engagement cover and synchronizer more at present, needs first cut-off clutch during the tractor gearshift, then speed changer is plucked neutral, block selecting again, gearshift, last engaging clutch.Like this, after clutch separation, before clutch engages again again, the power of motor can not be passed to wheel and go to drive the tractor operation, so produced the interruption of transmission of power in the shift process, gearshift slowly influences operating efficiency.Double-clutch automatic gearbox is a kind of novel automatic transmission; It with transmission gear by strange, even number is arranged in two two input shafts that clutch connected on; Accomplish the gearshift overshoot through alternately switching of clutch; Realized power gear shifting, this is particularly important concerning the tractor of on-load operation.
The concrete structure of existing dual-clutch transmission such as Chinese patent CN200410070324.9 disclosed a kind of " double clutch gearbox "; Comprise the input shaft that two coaxial settings and the output shaft through each self-corresponding clutch and corresponding motor are in transmission connection, double clutch gearbox also comprises reverse gear idler shaft and two jack shafts that laterally arrange with input shaft.Fixedly be equipped with the odd number gear driving gear (one, three retaining driving gears) that is used for the transmission of odd number gear on the input shaft in two input shafts; Fixedly be equipped with the even number gear driving gear (two, four retaining driving gears) that is used for the transmission of even number gear on another input shaft.Synchronizer through correspondence on one of them jack shaft on two jack shafts is connected with one, two, three and four retaining driven gears; Synchronizer through correspondence on another jack shaft is connected with five, six retaining and the driven gears that reverse gear.Wherein a retaining driving gear and a retaining driven gear mesh with the driven gear that reverses gear simultaneously; Two retaining driving gears are meshed with two retaining driven gears; Three retaining driving gears and three retaining driven gears and five retaining driven gears mesh simultaneously; Four retaining driving gears and four retaining driven gears and six retaining driven gears mesh simultaneously.Two jack shafts can be selected to be in transmission connection with corresponding driven gear through the corresponding synchronous device as required, and the output terminal of two jack shafts directly is in transmission connection with corresponding differential mechanism.The problem that existing dual-clutch transmission exists is: the cooperation of reversing gear between the idle pulley of installing on the driven gear that need reverse gear, reverse gear idler shaft and the corresponding idler shaft that reverses gear could be accomplished the process that corresponding vehicle reverses gear; The idler shaft that reverses gear makes not only with the use of idle pulley of reversing gear that the double-clutch speed changer occupation space is big, structure is not compact; Also increase the amount of parts of double-clutch speed changer, and then increased the cost of production and the installation difficulty of double-clutch speed changer.
Summary of the invention
The objective of the invention is to be to provide a kind of structure double-clutch speed changer of compactness more.
In order to address the above problem, technological scheme of the present invention is:
The dual-clutch transmission that uses in a kind of tractor; Comprise case of transmission; Be provided with input shaft that two coaxial settings and the output shaft through each self-corresponding clutch and corresponding motor be in transmission connection and first jack shaft and second jack shaft that laterally arranges with said input shaft in the case of transmission, wherein fixedly be equipped with the odd number gear driving gear that is used for the transmission of odd number gear on an input shaft; Fixedly be equipped with the even number gear driving gear that is used for the transmission of even number gear on another input shaft, be set with on described first jack shaft with corresponding input shaft on the first driven tooth wheels that selectively are in transmission connection with said first jack shaft of driving gear engagement driving and the synchronizer through corresponding setting on said first jack shaft; Be set with on described second jack shaft with corresponding input shaft on the second driven tooth wheels that driving gear is in transmission connection and synchronizer and said second jack shaft through corresponding setting on said second jack shaft selectively is in transmission connection with reverse gear driven gear; Be respectively equipped with on first and second jack shaft and be used for the outwards moment of torsion output section of output of corresponding moment of torsion, one of them the driven gear engagement driving in described reverse gear driven gear and the said first driven tooth wheels.
Input shaft and the coaxial outer input shaft that is sheathed on said interior input shaft periphery in described two input shafts comprise; Described clutch comprises first clutch, second clutch and the three-clutch that coaxial line is set up in parallel, and described interior input shaft is realized being in transmission connection with the output shaft of corresponding motor through second clutch; Described outer input shaft is realized being in transmission connection with the output shaft of corresponding motor through three-clutch; Described speed changer also is included in the load output shaft that coaxial output shaft that wear and through said first clutch and corresponding motor is in transmission connection in the input shaft in said, and said load output shaft is provided with the load power output section that is used for to the respective load outputting power.
Input shaft and the coaxial outer input shaft that is sheathed on said interior input shaft periphery in described two input shafts comprise; Described driving gear comprise the I, the III that are fixed on the said outer input shaft keep off shared driving gear and V, VII keep off shared driving gear and be fixed on said in IV, VI on the input shaft keep off shared driving gear and II, the shared driving gear that reverses gear, the described first driven tooth wheels comprise that empty cover is installed on III retaining driven gear, VII retaining driven gear, II retaining driven gear and the VI retaining driven gear on said first jack shaft; The described second driven tooth wheels comprise that the sky cover is installed on I retaining driven gear, V retaining driven gear and the IV retaining driven gear on said second jack shaft, and described synchronizer comprises that being installed on also can select III, the VII retaining synchronizer that is in transmission connection with said III retaining driven gear and VII retaining driven gear as required and can select as required on said first jack shaft keeps off II, the VI retaining synchronizer that driven gear is in transmission connection with said II retaining driven gear and VI; Described synchronizer also comprise be installed on said second jack shaft and can according to need select I, the V retaining synchronizer that is in transmission connection with said I retaining driven gear and V retaining driven gear and can select to keep off IV that driven gear and reverse gear be in transmission connection as required with IV, synchronizer reverses gear.
Described driven gear and the described II retaining driven gear engagement driving of reversing gear.
Beneficial effect of the present invention is: when tractor reverses gear operation; One of them driven gear in the first driven tooth wheels uses as the idle pulley that reverses gear, and first jack shaft uses as the idler shaft that reverses gear, and has saved the layout of original the reverse gear idle pulley and the idler shaft that reverses gear; Make structure compact more; Reduce amount of parts, saved fabricating cost, reduced installation difficulty.
Description of drawings
Fig. 1 is the structural representation of the embodiment of the invention;
Fig. 2 is that the A of Fig. 1 is to section face figure.
Embodiment
The embodiment of the dual-clutch transmission that uses in a kind of tractor is shown in Fig. 1 ~ 2: comprise clutch device, case of transmission 3, control system of speed variator.
Clutch device comprises first clutch C1, second clutch C2, the three-clutch C3 that the clutch device input shaft 2 that links to each other with motor 1 bent axle and coaxial line are set up in parallel.
Be provided with speed changer main tank part and secondary box of gearbox part in the case of transmission 3, speed changer main tank part comprises outer input shaft 30, interior input shaft 32, load output shaft 19, first jack shaft 6, second jack shaft 22, main output shaft 10.Outer input shaft 30 1 ends are connected with three-clutch C3, and interior input shaft 32 1 ends are connected with second clutch C2, and load output shaft 19 1 ends are connected with clutch first clutch C1.Outer input shaft 30, interior input shaft 32 and the rotation of load output shaft 19 coaxial lines.Adopt space parallel to arrange between outer input shaft 30, interior input shaft 32, load output shaft 19 and first jack shaft 6, second jack shaft 22.
Be installed with I on the outer input shaft 30, III is kept off shared driving gear 31, V, VII are kept off shared driving gear 28.Be installed with IV on the interior input shaft 32, VI is kept off shared driving gear 25, II, shared driving gear 21 reverses gear.Load output shaft 19 is provided with the load power output section that is used for to corresponding agricultural machinery and implement even load outputting power; Load output shaft 19 is used for the part of tractor engine power consequently all is delivered to the agricultural machinery and implement even load with the mode of rotating mechanical energy, drives agricultural machinery and implement work.
Be installed with III, VII retaining synchronizer S1 on first jack shaft 6; II, VI retaining synchronizer S2; And first power output gear 20 that is used for the output of main tank power; Empty cover is equipped with the first driven tooth wheels, and the first driven tooth wheels comprise III retaining driven gear 4, VII retaining driven gear 5, VI retaining driven gear 7, II retaining driven gear 8.III retaining driven gear 4 keeps off shared driving gear 31 engagement driving with I, III; VII retaining driven gear 5 keeps off shared driving gear 28 engagement driving with V, VII; VI retaining driven gear 7 keeps off shared driving gear 25 engagement driving with IV, VI, II retaining driven gear 8 and II, shared driving gear 21 engagement driving of reversing gear.III, VII retaining synchronizer S1 optionally is delivered to the moment of torsion that III is kept off driven gear 4, VII retaining driven gear 5 on first jack shaft 6.II, VI retaining synchronizer S2 optionally is delivered to the moment of torsion that II is kept off driven gear 8, VI retaining driven gear 7 on first jack shaft 6.
Be installed with I, V retaining synchronizer S3 on second jack shaft 22; IV, synchronizer S4 reverses gear; And second power output gear 23 that is used for the output of main tank power; Empty cover is equipped with the second driven tooth wheels and comprises I retaining driven gear 29, V retaining driven gear 27 and IV retaining driven gear 26 with driven gear 24, the second driven tooth wheels that reverse gear.Wherein I retaining driven gear 29 keeps off shared driving gear 31 engagement driving with I, III; V retaining driven gear 27 keeps off shared driving gear 28 engagement driving with V, VII; IV retaining driven gear 26 keeps off shared driving gear 25 engagement driving with IV, VI; Reverse gear driven gear 24 and II retaining driven gear 8 engagement driving.I, V retaining synchronizer S3 optionally is delivered to the moment of torsion that I is kept off driven gear 29, V retaining driven gear 27 on second jack shaft 22, IV, reverse gear synchronizer S4 optionally with IV keep off driven gear 26, the moment of torsion of the driven gear 24 that reverses gear is delivered on second jack shaft 22.II retaining driven gear 8 uses as the idle pulley that reverses gear simultaneously, has saved the layout of the reverse gear idler shaft and the idle pulley that reverses gear, and makes structure compact more, has reduced amount of parts.In other embodiments of the invention, reverse gear driven gear 8 can also keep off driven gear 4, VII retaining driven gear 5 or VI retaining driven gear 7 engagement driving with III.
Be installed with active force driven gear 9 on the main output shaft 10; This gear simultaneously with first jack shaft 6 on first power output gear 20 and second power output gear, 23 engagements on second jack shaft 22, optionally moment of torsion of each retaining of main tank is delivered on the main output shaft 10 through synchronizer S1, S2, S3, S4.Main output shaft 10 uses as the secondary box of gearbox input shaft simultaneously.
The secondary box of gearbox part comprises that odd-side input shaft (also being main output shaft 10 simultaneously), the sun gear 11 of planetary gears, planet wheel 17, planet carrier 16, ring gear 18, height keep off synchronizer S5, secondary output shaft 14, the synchronous awl of high retaining and low retaining and bore 12 synchronously.Sun gear 11 coaxial being fixedly mounted on the odd-side input shaft.Be installed with planet carrier 16 on the secondary output shaft 14, also be provided with the driving dynamics output section that is used for the power of speed changer is exported to propons or back axle on the secondary output shaft.Be equipped with on the driving dynamics output section with power reach propons 53 driving gear 15 (be installed with on it high retaining synchronously awl), output power to the drive bevel gear 13 of back axle 54.Ring gear 18 keeps off synchronizer S5 with height and is fixed into a rigid unitary.Low retaining awl 12 synchronously is connected on the case of transmission 3 through certain device, and high retaining awl synchronously is fixed together with the driving gear 15 that power is reached propons 53.Height keeps off synchronizer S5 and optionally the transmission of power of odd-side input shaft 10 is arrived secondary output shaft 14.In other embodiments of the invention, speed changer main tank part and secondary box of gearbox part can also be divided in two housings.
Control system of speed variator be included in rotating speed that being used to of being provided with on the other case of transmission 3 of load output shaft 19, interior input shaft 32, outer input shaft 30, first jack shaft 6, second jack shaft 22 and secondary output shaft 14 detect each corresponding shaft with the running state of speed changer is discerned with the speed probe of judging 33, the electronic control unit (ECU) 50 that is connected with each speed probe 33, the clutch operation 51 that is connected with each Clutch Control and with each synchronizer control connection select shift control mechanism 52, clutch operation 51 and select shift control mechanism 52 control connections.During work; The sensor (not shown) of each speed probe 33 and other type is discerned the running state of speed changer and is judged; According to the schedule of setting, when the needs gear shift operation, electronic control unit (ECU) 50 sends instruction; Through clutch operation 51 with select shift control mechanism 52 to control the operation of each clutch and each synchronizer gearshift action, realization automatic speed changing respectively.
The speed changer main tank of dual-clutch transmission of the present invention comprises that partly seven forward gears and one reverses gear; Secondary box of gearbox partly comprises high and low two retainings; Can obtain (7+1) * 2 retaining through the major and minor case part of speed changer gear collocation, promptly 14 forward gears, 2 reverse gear.Gear is more, can satisfy the requirement of different tractor operation operating modes to speed, and each gear power transmission line of the major and minor case part of speed changer is:
Main tank I retaining: three-clutch C3 engages, and I, V retaining synchronizer S3 and I retaining driven gear 29 engage.Through this joint; Engine torque is passed to outer input shaft 30 through three-clutch C3; Moment of torsion keeps off shared driving gear 31, I retaining driven gear 29, I, V retaining synchronizer S3 via I, III and is passed to second jack shaft 22 then, and final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via second power output gear 23, active force driven gear 9.
Main tank II retaining: second clutch C2 engages, and II, VI retaining synchronizer S2 and II retaining driven gear 8 engage.Through this joint; Input shaft 32 in Engine torque is passed to through second clutch C2; Moment of torsion is passed to first jack shaft 6 via II, the shared driving gear 21 that reverses gear, II retaining driven gear 8, II, VI retaining synchronizer S2 then, and final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via first power output gear 20, active force driven gear 9.
Main tank III retaining: three-clutch C3 engages, and III, VII retaining synchronizer S1 and III retaining driven gear 4 engage.Through this joint; Engine torque is passed to outer input shaft 30 through three-clutch C3; Moment of torsion keeps off shared driving gear 31, III retaining driven gear 4, III, VII retaining synchronizer S1 via I, III and is passed to first jack shaft 6 then, and final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via first power output gear 20, active force driven gear 9.
Main tank IV retaining: second clutch C2 engages, and IV, reverse gear synchronizer S4 and IV retaining driven gear 26 engage.Through this joint; Input shaft 32 in Engine torque is passed to through second clutch C2; Moment of torsion keeps off shared driving gear 25, IV retaining driven gear 26, IV, the synchronizer S4 that reverses gear via IV, VI and is passed to second jack shaft 22 then, and final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via second power output gear 23, active force driven gear 9.
Main tank V retaining: three-clutch C3 engages, and I, V retaining synchronizer S3 and V retaining driven gear 27 engage.Through this joint; Engine torque is passed to outer input shaft 30 through three-clutch C3; Moment of torsion keeps off shared driving gear 28, V retaining driven gear 27, I, V retaining synchronizer S3 via V, VII and is passed to second jack shaft 22 then, and final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via second power output gear 23, active force driven gear 9.
Main tank VI retaining: second clutch C2 engages, and II, VI retaining synchronizer S2 and VI retaining driven gear 7 engage.Through this joint; Input shaft 32 in Engine torque is passed to through second clutch C2; Moment of torsion keeps off shared driving gear 25, VI retaining driven gear 7, II, VI retaining synchronizer S2 via IV, VI and is passed to first jack shaft 6 then, and final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via first power output gear 20, active force driven gear 9.
Main tank VII retaining: three-clutch C3 engages, and III, VII retaining synchronizer S1 and VII retaining driven gear 5 engage.Through this joint; Engine torque is passed to outer input shaft 30 through clutch C3; Moment of torsion keeps off shared driving gear 28, VII retaining driven gear 5, synchronizer S1 via V, VII and is passed to first jack shaft 6 then, and final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via first power output gear 20, active force driven gear 9.
Main tank reverses gear: second clutch C2 engages, and IV, reverse gear synchronizer S4 and the driven gear 24 that reverses gear engage.Through this joint; Input shaft 32 in Engine torque is passed to through clutch C2; Moment of torsion is passed to second jack shaft 22 via II, the shared driving gear 21 that reverses gear, the idle pulley that reverses gear (simultaneously as II retaining driven gear 8), the driven gear 24 that reverses gear, IV, the synchronizer S4 that reverses gear then, and final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via second power output gear 23, active force driven gear 9.
The low retaining of odd-side: height keeps off synchronizer S5 and hangs down retaining awl 12 joints synchronously, ring gear 18 lockings of planetary gears.Through this joint; The moment of torsion of main tank part is passed to secondary output shaft 14 via odd-side input shaft (also being main output shaft 10 simultaneously), sun gear 11, planet wheel 17, planet carrier 16; Final torque is passed to back axle 54 through drive bevel gear 13, perhaps is passed to propons 53 through driving gear 15.
The high retaining of odd-side: height keeps off synchronizer S5 and engages with the synchronous bevel gear 15 of high retaining, make the synchronous bevel gear of high retaining 15, height keep off synchronizer S5, secondary output shaft 14, planet carrier 17, ring gear 18 and become one, thereby whole planetary gears is an integral body.Through this joint; The moment of torsion of main tank part is passed to secondary output shaft 14 via odd-side input shaft (also being main output shaft 10 simultaneously), planetary gears; Final torque is passed to back axle 54 through drive bevel gear 13, perhaps is passed to propons 53 through driving gear 15.

Claims (4)

1. the dual-clutch transmission that uses in the tractor; Comprise case of transmission; Be provided with input shaft that two coaxial settings and the output shaft through each self-corresponding clutch and corresponding motor be in transmission connection and first jack shaft and second jack shaft that laterally arranges with said input shaft in the case of transmission, wherein fixedly be equipped with the odd number gear driving gear that is used for the transmission of odd number gear on an input shaft; Fixedly be equipped with the even number gear driving gear that is used for the transmission of even number gear on another input shaft, be set with on described first jack shaft with corresponding input shaft on the first driven tooth wheels that selectively are in transmission connection with said first jack shaft of driving gear engagement driving and the synchronizer through corresponding setting on said first jack shaft; Be set with on described second jack shaft with corresponding input shaft on the second driven tooth wheels that driving gear is in transmission connection and synchronizer and said second jack shaft through corresponding setting on said second jack shaft selectively is in transmission connection with reverse gear driven gear; Be respectively equipped with the moment of torsion output section that is used for the outside output of corresponding moment of torsion on first and second jack shaft, it is characterized in that: one of them the driven gear engagement driving in described reverse gear driven gear and the said first driven tooth wheels.
2. dual-clutch transmission according to claim 1; It is characterized in that: input shaft and the coaxial outer input shaft that is sheathed on said interior input shaft periphery in described two input shafts comprise; Described clutch comprises first clutch, second clutch and the three-clutch that coaxial line is set up in parallel, and described interior input shaft is realized being in transmission connection with the output shaft of corresponding motor through second clutch; Described outer input shaft is realized being in transmission connection with the output shaft of corresponding motor through three-clutch; Described speed changer also is included in the load output shaft that coaxial output shaft that wear and through said first clutch and corresponding motor is in transmission connection in the input shaft in said, and said load output shaft is provided with the load power output section that is used for to the respective load outputting power.
3. dual-clutch transmission according to claim 1; It is characterized in that: input shaft and the coaxial outer input shaft that is sheathed on said interior input shaft periphery in described two input shafts comprise; Described driving gear comprise the I, the III that are fixed on the said outer input shaft keep off shared driving gear and V, VII keep off shared driving gear and be fixed on said in IV, VI on the input shaft keep off shared driving gear and II, the shared driving gear that reverses gear, the described first driven tooth wheels comprise that empty cover is installed on III retaining driven gear, VII retaining driven gear, II retaining driven gear and the VI retaining driven gear on said first jack shaft; The described second driven tooth wheels comprise that the sky cover is installed on I retaining driven gear, V retaining driven gear and the IV retaining driven gear on said second jack shaft, and described synchronizer comprises that being installed on also can select III, the VII retaining synchronizer that is in transmission connection with said III retaining driven gear and VII retaining driven gear as required and can select as required on said first jack shaft keeps off II, the VI retaining synchronizer that driven gear is in transmission connection with said II retaining driven gear and VI; Described synchronizer also comprise be installed on said second jack shaft and can according to need select I, the V retaining synchronizer that is in transmission connection with said I retaining driven gear and V retaining driven gear and can select to keep off IV that driven gear and reverse gear be in transmission connection as required with IV, synchronizer reverses gear.
4. dual-clutch transmission according to claim 3 is characterized in that: described driven gear and the described II retaining driven gear engagement driving of reversing gear.
CN201110405943.9A 2011-12-08 2011-12-08 Double-clutch transmission used in tractor Expired - Fee Related CN102678839B (en)

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CN102678839B CN102678839B (en) 2015-05-13

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CN103256355B (en) * 2013-04-28 2015-07-15 河南科技大学 Double-planet-row converging type multi-clutch transmission
CN103256350A (en) * 2013-04-28 2013-08-21 河南科技大学 Multi-gear multi-clutch speed changer
CN103277466A (en) * 2013-04-28 2013-09-04 河南科技大学 Multi-clutch speed changer
CN103256355A (en) * 2013-04-28 2013-08-21 河南科技大学 Double-planet-row converging type multi-clutch transmission
CN103277466B (en) * 2013-04-28 2015-07-15 河南科技大学 Multi-clutch speed changer
US9568082B2 (en) 2014-01-30 2017-02-14 Byd Company Limited Power transmission system for vehicle and vehicle comprising the same
US9944165B2 (en) 2014-01-30 2018-04-17 Byd Company Limited Power transmission system for vehicle and vehicle comprising the same
WO2015113423A1 (en) * 2014-01-30 2015-08-06 比亚迪股份有限公司 Vehicle and power transmission system thereof
WO2015113414A1 (en) * 2014-01-30 2015-08-06 Byd Company Limited Power transmission system for vehicle and vehicle comprising the same
WO2015113422A1 (en) * 2014-01-30 2015-08-06 比亚迪股份有限公司 Vehicle and power transmission system thereof
US10670123B2 (en) 2014-01-30 2020-06-02 Byd Company Limited Power transmission system for vehicle and vehicle comprising the same
US10363806B2 (en) 2014-01-30 2019-07-30 Byd Company Limited Power transmission system for vehicle and vehicle comprising the same
WO2015113424A1 (en) * 2014-01-30 2015-08-06 比亚迪股份有限公司 Vehicle and power transmission system thereof
US9568080B2 (en) 2014-01-30 2017-02-14 Byd Company Limited Power transmission system for vehicle and vehicle comprising the same
US9919699B2 (en) 2014-01-30 2018-03-20 Byd Company Limited Vehicle and method for controlling synchronizer of the same
US9568081B2 (en) 2014-01-30 2017-02-14 Byd Company Limited Power transmission system for vehicle and vehicle comprising the same
US9566978B2 (en) 2014-01-30 2017-02-14 Byd Company Limited Vehicle and drive control method for the same
EP3100886A4 (en) * 2014-01-30 2017-06-28 BYD Company Limited Vehicle and power transmission system thereof
CN103982605A (en) * 2014-04-16 2014-08-13 河南科技大学 Shift mechanism and double-clutch combined transmission and vehicle using shift mechanism
CN103982605B (en) * 2014-04-16 2016-07-06 河南科技大学 Shifter and use double; two clutch combined speed changers and the vehicle of this shifter
US9568065B2 (en) 2014-09-10 2017-02-14 Byd Company Limited Transmission unit, power transmission system and vehicle comprising the same
US9874266B2 (en) 2014-09-10 2018-01-23 Byd Company Limited Power transmission system and vehicle comprising the same
US9568066B2 (en) 2014-09-10 2017-02-14 Byd Company Limited Power transmission system and vehicle comprising the same
US9421966B2 (en) 2014-10-20 2016-08-23 Byd Company Limited Hybrid vehicle and shifting control method and power transmission system thereof
CN111328367A (en) * 2017-11-09 2020-06-23 凯斯纽荷兰(中国)管理有限公司 Improvements in or relating to dual clutch transmissions
CN111328367B (en) * 2017-11-09 2023-01-17 凯斯纽荷兰(中国)管理有限公司 Improvements in or relating to dual clutch transmissions

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