CN102678847B - Dual-clutch transmission for tractor - Google Patents
Dual-clutch transmission for tractor Download PDFInfo
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- CN102678847B CN102678847B CN2011104059424A CN201110405942A CN102678847B CN 102678847 B CN102678847 B CN 102678847B CN 2011104059424 A CN2011104059424 A CN 2011104059424A CN 201110405942 A CN201110405942 A CN 201110405942A CN 102678847 B CN102678847 B CN 102678847B
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 71
- 230000001360 synchronised effect Effects 0.000 claims abstract description 35
- 239000000523 sample Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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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 parallel flow paths, e.g. dual clutch transmissions
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Abstract
本发明涉及一种用于拖拉机的双离合器变速器，包括输入轴、中间轴及与中间轴传动连接的主输出轴，主输出轴上传动连接有高低挡换挡机构，高低挡换挡机构包括高、低挡同步锥齿轮、副输出轴及行星齿轮机构；一个同步锥齿轮固连于变速器壳体上，另一个同步锥齿轮固连于副输出轴上，行星齿轮机构包括行星架、行星轮及太阳轮和内齿圈，太阳轮与主输出轴同轴固连，高低挡换挡机构还包括与内齿圈固连并可根据需要可选择的与高或低挡同步锥齿轮传动连接的高低挡同步器，副输出轴上设有用于将变速器的动力向外输出的行驶动力输出段。本发明提供了一种具有高、低挡输出的用于拖拉机的双离合器变速器，可满足拖拉机在不同作业工况时对速度的要求。
The invention relates to a dual-clutch transmission for tractors, which includes an input shaft, an intermediate shaft and a main output shaft connected to the intermediate shaft. The main output shaft is connected with a high-low gear shifting mechanism. , low-speed synchronous bevel gear, auxiliary output shaft and planetary gear mechanism; one synchronous bevel gear is fixedly connected to the transmission case, and the other synchronous bevel gear is fixedly connected to the auxiliary output shaft. The planetary gear mechanism includes a planetary carrier, planetary wheels and The sun gear and the inner ring gear, the sun gear is coaxially connected with the main output shaft, and the high-low gear shifting mechanism also includes a high-low gear that is fixedly connected with the inner ring gear and can be connected with high or low gear synchronous bevel gear transmission according to needs. gear synchronizer, and the auxiliary output shaft is provided with a driving power output section for outputting the power of the transmission to the outside. The invention provides a dual-clutch transmission for a tractor with high and low gear outputs, which can meet the speed requirements of the tractor under different operating conditions.
Description
Technical field
The present invention relates to the speed changer technical field, relate in particular to a kind of dual-clutch transmission that is used for 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, finish the gearshift overshoot by 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 by 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 be arranged in parallel 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 by correspondence on one of them jack shaft on two jack shafts is connected with one, two, three and four retaining driven gears; Synchronizer by 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 and the driven gear that reverses gear mesh 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 by 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: though four driving gears on two input shafts can realize that by the synchronizer of correspondence six forward gears and one reverses gear, but the output of the gear of this double clutch gearbox does not have the function of high to low gear output, because the various operating modes that tractor runs into when work are more, it is this to the special vehicle of working condition requirement to make that existing dual-clutch transmission just can not adapt to tractor.
Summary of the invention
The object of the present invention is to provide a kind of dual-clutch transmission that is used for tractor with high and low retaining output.
In order to address the above problem, technological scheme of the present invention is:
A kind of dual-clutch transmission that is used for tractor, comprise case of transmission, be provided with clutch and two input shafts in the case of transmission, clutch comprises second clutch and the three-clutch that coaxial line is set up in parallel, input shaft and the coaxial outer input shaft that is sheathed on described interior input shaft periphery in two input shafts comprise, interior input shaft is in transmission connection by the output shaft of second clutch and corresponding motor, outer input shaft is in transmission connection by the output shaft of three-clutch and described motor, 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, also be provided with two jack shafts that be arranged in parallel with described interior input shaft in the case of transmission, all be set with on two jack shafts by the selectable driven gear that is in transmission connection with corresponding jack shaft of the synchronizer of each jack shaft setting, each driven gear is in transmission connection with corresponding driving gear respectively, described speed changer also comprises the main output shaft that be arranged in parallel with input shaft, fixedly be equipped with active force on the main output shaft from nutating gear, fixedly be equipped with while and first power output gear and second power output gear of described active force on described two jack shafts respectively from the nutating gear engagement driving, be connected with the high to low gear gearshift on the described main output shaft, described high to low gear gearshift comprises the synchronous bevel gear of high gear, the synchronous bevel gear of low gear, with the secondary output shaft of the coaxial setting of described main output shaft and the planetary gears that is in transmission connection with described secondary output shaft, described height, a synchronous bevel gear in the synchronous bevel gear of low gear is fixed on the described case of transmission; Another synchronous bevel gear is coaxial to be fixed on the described secondary output shaft, described planetary gears comprises the planet carrier with described secondary output shaft fixed connection, rotation be assemblied on the planet carrier planet wheel and respectively with the sun gear and the ring gear of described planet wheel engagement driving, described sun gear is connected with described main output shaft is coaxial, described high to low gear gearshift also comprises the high to low gear synchronizer that is connected and can selects as required to be connected with synchronous bevel gear of described high gear or the synchronous bevel gear drive of low gear with described ring gear, also is 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 described secondary output shaft.
Described clutch also comprises the first clutch that is set up in parallel with the second clutch coaxial line, described speed changer also is included in the load output shaft that coaxial output shaft that wear and by described first clutch and described motor is in transmission connection in the input shaft in described, and described load output shaft is provided with the load power output section that is used for to the respective load outputting power.
Synchronous bevel gear of described high gear and coaxial being connected of described secondary output shaft, the synchronous bevel gear of described low gear is fixed on the described case of transmission, described driving dynamics output section is provided with and is used for the drive bevel gear that the back axle with corresponding tractor is in transmission connection, and is fixed with the power that is used for speed changer on the synchronous bevel gear of described high gear and exports propons driving gear on the propons of corresponding tractor to.
Described driving gear comprises the I that is fixed on the described outer input shaft, III is kept off shared driving gear and V, VII keep off shared driving gear and be fixed on described in IV on the input shaft, VI is kept off shared driving gear and II, shared driving gear reverses gear, described two jack shafts are respectively first jack shaft and second jack shaft, described synchronizer comprises the III that is installed on described first jack shaft, VII retaining synchronizer and II, VI retaining synchronizer and be installed on I on described second jack shaft, V retaining synchronizer and IV, synchronizer reverses gear, described driven gear is included in the selectable as required and described III that the overhead cover of described first jack shaft is installed, the III retaining driven gear that VII retaining synchronizer is in transmission connection and VII retaining driven gear and selectable as required and described II, II retaining driven gear that VI retaining synchronizer is in transmission connection and VI retaining driven gear, described driven gear also is included in the selectable as required and described I that the overhead cover of described second jack shaft is installed, the I retaining driven gear that V retaining synchronizer is in transmission connection and V retaining driven gear and selectable as required and IV, the IV retaining driven gear that the synchronizer that reverses gear is in transmission connection and the driven gear that reverses gear, described I retaining driven gear and III retaining driven gear while and described I, III is kept off shared driving gear engagement driving, described V retaining driven gear and VII retaining driven gear while and described V, VII is kept off shared driving gear engagement driving, described IV retaining driven gear and VI retaining driven gear while and described IV, VI is kept off shared driving gear engagement driving, described II retaining driven gear and described II, the shared driving gear engagement driving of reversing gear.
Described II retaining driven gear and the described driven gear engagement driving of reversing gear.
Beneficial effect of the present invention is: when tractor needs the low gear operation, synchronous bevel gear engages for high to low gear synchronizer and low gear, by this joint, the moment of torsion of one of them jack shaft is passed to secondary output shaft via main output shaft, sun gear, planet wheel, planet carrier in two jack shafts, be passed to the propons or the back axle of corresponding tractor at last, thereby realize the low gear operation of motor; When tractor needs the high gear operation, synchronous bevel gear engages for high to low gear synchronizer and high gear, by this joint, the moment of torsion of one of them jack shaft is passed to secondary output shaft via main output shaft, sun gear, planet wheel, planet carrier in two jack shafts, be passed to the propons or the back axle of corresponding tractor at last, thereby realize the high gear operation of motor.By carrying out the handover operation of high to low gear, can satisfy tractor requirement to speed when the different work operating mode.
Further, when tractor reversed gear operation, II retaining driven gear used as the idle pulley that reverses gear simultaneously, has saved the layout of the reverse gear idle pulley and the idler shaft that reverses gear, and made structure compact more, had reduced amount of parts, saved fabricating cost, had reduced installation difficulty.
Description of drawings
Fig. 1 is the structural representation of the embodiment of the invention;
Fig. 2 is that A-A among Fig. 1 is to sectional view.
Embodiment
A kind of embodiment of the dual-clutch transmission that is used for 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 in 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 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.The moment of torsion that III, VII retaining synchronizer S1 optionally keep off III driven gear 4, VII retaining driven gear 5 is delivered on first jack shaft 6.The moment of torsion that II, VI retaining synchronizer S2 optionally keep off II driven gear 8, VI retaining driven gear 7 is delivered 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 I retaining driven gear 29, V retaining driven gear 27, IV retaining driven gear 26, driven gear 24 reverses 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.The moment of torsion that I, V retaining synchronizer S3 optionally keep off I driven gear 29, V retaining driven gear 27 is delivered on second jack shaft 22, and the moment of torsion that IV, the synchronizer S4 that reverses gear optionally keep off IV driven gear 26, 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.Certainly in other embodiments of the invention, also can adopt the form of arranging the reverse gear idler shaft and the idle pulley that reverses gear to realize the operation of reversing gear of speed changer.
Be installed with active force on the main output shaft 10 from nutating gear 9, 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 by synchronizer S1, S2, S3, S4.Main output shaft 10 uses as the input shaft of secondary box of gearbox part simultaneously.
The secondary box of gearbox part, comprise the high to low gear gearshift that is in transmission connection with main output shaft 10, the height gearshift comprises sun gear 11, planet wheel 17, planet carrier 16, ring gear 18, high to low gear synchronizer S5, secondary output shaft 14, the synchronous bevel gear of high gear and the synchronous bevel gear 12 of low gear of planetary gears.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.The driving gear 15(that power is reached propons 53 is installed on the driving dynamics output section is installed with the synchronous bevel gear of high gear on it), output power to the drive bevel gear 13 of back axle 54.Ring gear 18 is fixed into a rigid unitary with high to low gear synchronizer S5.The synchronous bevel gear 12 of low gear is connected on the case of transmission 3 by certain device, and the synchronous bevel gear of high gear is fixed together with the driving gear 15 that power is reached propons 53.High to low gear synchronizer S5 optionally arrives secondary output shaft 14 with the transmission of power of odd-side input shaft 10.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 is included in load output shaft 19, interior input shaft 32, outer input shaft 30, first jack shaft 6, the speed probe 33 of rotating speed that is used to detect each corresponding shaft that is provided with on the case of transmission 3 on second jack shaft 22 and secondary output shaft 14 sides so that the running state of speed changer is discerned and judged, 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 shifting operating mechanism 52, clutch operation 51 and shifting operating mechanism 52 control connections of each synchronizer control connection.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, control the operation of each clutch and each synchronizer gearshift action respectively by clutch operation 51 and shifting operating mechanism 52, realize automatic speed changing.
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 by 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 tractor different work operating mode 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.By this joint, Engine torque is passed to outer input shaft 30 by 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 from nutating gear 9.
Main tank II retaining: second clutch C2 engages, and II, VI retaining synchronizer S2 and II retaining driven gear 8 engage.By this joint, input shaft 32 in Engine torque is passed to by 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 from nutating gear 9.
Main tank III retaining: three-clutch C3 engages, and III, VII retaining synchronizer S1 and III retaining driven gear 4 engage.By this joint, Engine torque is passed to outer input shaft 30 by 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 from nutating gear 9.
Main tank IV retaining: second clutch C2 engages, and IV, reverse gear synchronizer S4 and IV retaining driven gear 26 engage.By this joint, input shaft 32 in Engine torque is passed to by second clutch C2, then moment of torsion via IV, VI keep off shared driving gear 25, IV retaining driven gear 26, IV, the synchronizer S4 that reverses gear is passed to second jack shaft 22, final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via second power output gear 23, active force from nutating gear 9.
Main tank V retaining: three-clutch C3 engages, and I, V retaining synchronizer S3 and V retaining driven gear 27 engage.By this joint, Engine torque is passed to outer input shaft 30 by 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 from nutating gear 9.
Main tank VI retaining: second clutch C2 engages, and II, VI retaining synchronizer S2 and VI retaining driven gear 7 engage.By this joint, input shaft 32 in Engine torque is passed to by 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 from nutating gear 9.
Main tank VII retaining: three-clutch C3 engages, and III, VII retaining synchronizer S1 and VII retaining driven gear 5 engage.By this joint, Engine torque is passed to outer input shaft 30 by clutch C3, then moment of torsion via V, VII keep off shared driving gear 28, VII retaining driven gear 5, synchronizer S1 is passed to first jack shaft 6, final torque is passed to odd-side input shaft (also being main output shaft 10 simultaneously) via first power output gear 20, active force from nutating 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.By this joint, input shaft 32 in Engine torque is passed to by 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 from nutating gear 9.
The odd-side low gear: the synchronous bevel gear 12 of high to low gear synchronizer S5 and low gear engages ring gear 18 lockings of planetary gears.By 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 by drive bevel gear 13, perhaps is passed to propons 53 by driving gear 15.
The odd-side high gear: the synchronous bevel gear 15 of high to low gear synchronizer S5 and high gear engages, and make the synchronous bevel gear 15 of high gear, high to low gear synchronizer S5, secondary output shaft 14, planet carrier 17, ring gear 18 become one, thereby whole planetary gears is an integral body.By 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 by drive bevel gear 13, perhaps is passed to propons 53 by driving gear 15.
Claims (5)
1. dual-clutch transmission that is used for tractor, comprise case of transmission, be provided with clutch and two input shafts in the case of transmission, clutch comprises second clutch and the three-clutch that coaxial line is set up in parallel, input shaft and the coaxial outer input shaft that is sheathed on described interior input shaft periphery in two input shafts comprise, interior input shaft is in transmission connection by the output shaft of second clutch and corresponding motor, outer input shaft is in transmission connection by the output shaft of three-clutch and described motor, 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, also be provided with two jack shafts that be arranged in parallel with described interior input shaft in the case of transmission, all be set with on two jack shafts by the selectable driven gear that is in transmission connection with corresponding jack shaft of the synchronizer of each jack shaft setting, each driven gear is in transmission connection with corresponding driving gear respectively, it is characterized in that: described speed changer also comprises the main output shaft that be arranged in parallel with input shaft, fixedly be equipped with active force on the main output shaft from nutating gear, fixedly be equipped with while and first power output gear and second power output gear of described active force on described two jack shafts respectively from the nutating gear engagement driving, be connected with the high to low gear gearshift on the described main output shaft, described high to low gear gearshift comprises the synchronous bevel gear of high gear, the synchronous bevel gear of low gear, with the secondary output shaft of the coaxial setting of described main output shaft and the planetary gears that is in transmission connection with described secondary output shaft, described height, a synchronous bevel gear in the synchronous bevel gear of low gear is fixed on the described case of transmission; Another synchronous bevel gear is coaxial to be fixed on the described secondary output shaft, described planetary gears comprises the planet carrier with described secondary output shaft fixed connection, rotation be assemblied on the planet carrier planet wheel and respectively with the sun gear and the ring gear of described planet wheel engagement driving, described sun gear is connected with described main output shaft is coaxial, described high to low gear gearshift also comprises the high to low gear synchronizer that is connected and can selects as required to be connected with synchronous bevel gear of described high gear or the synchronous bevel gear drive of low gear with described ring gear, also is 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 described secondary output shaft.
2. dual-clutch transmission according to claim 1, it is characterized in that: described clutch also comprises the first clutch that is set up in parallel with the second clutch coaxial line, described speed changer also is included in the load output shaft that coaxial output shaft that wear and by described first clutch and described motor is in transmission connection in the input shaft in described, and described 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: synchronous bevel gear of described high gear and coaxial being connected of described secondary output shaft, the synchronous bevel gear of described low gear is fixed on the described case of transmission, described driving dynamics output section is provided with and is used for the drive bevel gear that the back axle with corresponding tractor is in transmission connection, and is fixed with the power that is used for speed changer on the synchronous bevel gear of described high gear and exports propons driving gear on the propons of corresponding tractor to.
4. dual-clutch transmission according to claim 1, it is characterized in that: described driving gear comprises the I that is fixed on the described outer input shaft, III is kept off shared driving gear and V, VII keep off shared driving gear and be fixed on described in IV on the input shaft, VI is kept off shared driving gear and II, shared driving gear reverses gear, described two jack shafts are respectively first jack shaft and second jack shaft, described synchronizer comprises the III that is installed on described first jack shaft, VII retaining synchronizer and II, VI retaining synchronizer and be installed on I on described second jack shaft, V retaining synchronizer and IV, synchronizer reverses gear, described driven gear is included in the selectable as required and described III that the overhead cover of described first jack shaft is installed, the III retaining driven gear that VII retaining synchronizer is in transmission connection and VII retaining driven gear and selectable as required and described II, II retaining driven gear that VI retaining synchronizer is in transmission connection and VI retaining driven gear, described driven gear also is included in the selectable as required and described I that the overhead cover of described second jack shaft is installed, the I retaining driven gear that V retaining synchronizer is in transmission connection and V retaining driven gear and selectable as required and IV, the IV retaining driven gear that the synchronizer that reverses gear is in transmission connection and the driven gear that reverses gear, described I retaining driven gear and III retaining driven gear while and described I, III is kept off shared driving gear engagement driving, described V retaining driven gear and VII retaining driven gear while and described V, VII is kept off shared driving gear engagement driving, described IV retaining driven gear and VI retaining driven gear while and described IV, VI is kept off shared driving gear engagement driving, described II retaining driven gear and described II, the shared driving gear engagement driving of reversing gear.
5. dual-clutch transmission according to claim 4 is characterized in that: described II retaining driven gear and the described driven gear engagement driving of reversing gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011104059424A CN102678847B (en) | 2011-12-08 | 2011-12-08 | Dual-clutch transmission for tractor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011104059424A CN102678847B (en) | 2011-12-08 | 2011-12-08 | Dual-clutch transmission for tractor |
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| Publication Number | Publication Date |
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| CN102678847A CN102678847A (en) | 2012-09-19 |
| CN102678847B true CN102678847B (en) | 2013-07-31 |
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| CN2011104059424A Expired - Fee Related CN102678847B (en) | 2011-12-08 | 2011-12-08 | Dual-clutch transmission for tractor |
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Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103256346B (en) * | 2013-04-28 | 2015-08-19 | 河南科技大学 | Planet row convergent current type multi-clutch speed changer |
| CN103256350B (en) * | 2013-04-28 | 2015-08-19 | 河南科技大学 | Many grades of multi-clutch speed changers |
| 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 |
| CN110259921B (en) * | 2018-10-30 | 2024-04-26 | 沈万伦 | Double-planetary-disc gearbox |
| CN109649164A (en) * | 2018-11-23 | 2019-04-19 | 安徽农业大学 | A kind of tractor motive power output shaft torque distribution control apparatus and method |
| CN116066530B (en) * | 2023-02-13 | 2025-06-20 | 潍柴动力股份有限公司 | Transmission system and transmission method |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3621545A1 (en) * | 1986-06-27 | 1988-01-28 | Tropp Axel Dipl Ing Fh | TWO CLUTCH POWERTRAINS |
| EP0797025A1 (en) * | 1996-03-21 | 1997-09-24 | LANDINI SpA | Under-load change-speed gear unit with double clutch |
| EP0987467A2 (en) * | 1998-09-15 | 2000-03-22 | DaimlerChrysler Corporation | Electro-mechanical automatic transmission having dual input shafts |
| CN202349119U (en) * | 2011-12-08 | 2012-07-25 | 河南科技大学 | Double-clutch transmission for tractor |
-
2011
- 2011-12-08 CN CN2011104059424A patent/CN102678847B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3621545A1 (en) * | 1986-06-27 | 1988-01-28 | Tropp Axel Dipl Ing Fh | TWO CLUTCH POWERTRAINS |
| EP0797025A1 (en) * | 1996-03-21 | 1997-09-24 | LANDINI SpA | Under-load change-speed gear unit with double clutch |
| EP0987467A2 (en) * | 1998-09-15 | 2000-03-22 | DaimlerChrysler Corporation | Electro-mechanical automatic transmission having dual input shafts |
| CN202349119U (en) * | 2011-12-08 | 2012-07-25 | 河南科技大学 | Double-clutch transmission for tractor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102678847A (en) | 2012-09-19 |
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