CN203902248U - Longitudinal hybrid dual-clutch transmission actuator - Google Patents
Longitudinal hybrid dual-clutch transmission actuator Download PDFInfo
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- CN203902248U CN203902248U CN201420258449.3U CN201420258449U CN203902248U CN 203902248 U CN203902248 U CN 203902248U CN 201420258449 U CN201420258449 U CN 201420258449U CN 203902248 U CN203902248 U CN 203902248U
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 28
- 230000007704 transition Effects 0.000 claims abstract description 49
- 230000007246 mechanism Effects 0.000 claims abstract description 19
- 229920000136 polysorbate Polymers 0.000 claims description 29
- 230000004044 response Effects 0.000 abstract description 3
- 238000000034 method Methods 0.000 description 5
- 230000008859 change Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 244000144983 clutch Species 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000001141 propulsive effect Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
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- 238000010586 diagram Methods 0.000 description 1
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Abstract
The utility model provides a longitudinal hybrid dual-clutch transmission actuator. Torque of a motor is directly transmitted to a middle shaft through a second planet gear mechanism and then transmitted to an output shaft, rather than a first clutch shell or a second clutch shell, through a transition shaft and a first planet gear mechanism. In this way, increasing of response speed is facilitated, and torque output loss, caused by gear ratio, of the first planet gear mechanism is made up.
Description
Technical field
The utility model relates to Automotive transmission field.
Background technology
The general vertical double clutch transmissions of putting is by two groups of coaxial nested or power-transfer clutchs of being arranged in parallel, coaxially, two of inside and outside nested arrangement input shafts, a tween drive shaft being arranged in parallel, an output shaft coaxially arranged with input shaft, is arranged in the multiple synchromesh gears on output shaft, multiple control fork composition.Change-speed box is strange, even number shelves input gear is arranged on two input shafts, by switching and the action of different synchro of two power-transfer clutchs, realizes torque conversion and output via different output shafts.Thereby in prior art, utilize sun and planet gear to change speed ratio and increase the numbers of gear steps that can realize, while adopting hybrid power, Motor torque is realized with the independent of engine power or is mixed output by first, second clutch-bell cover, now Motor torque output can be subject to bang path, sun and planet gear changes the adverse effect of speed ratio, and then affects car load power output performance.
Utility model content
The purpose of this utility model is to provide the more steadily vertical pair clutch gearbox drivings device of putting of failure-free hybrid power of a kind of power output, and embodiment of the present utility model provides following technical scheme for this reason:
The vertical pair clutch gearbox drivings device of putting of a kind of hybrid power, comprising: first clutch and second clutch; The interior input shaft being connected with described first clutch and the outer input shaft being connected with described second clutch, described interior input shaft is coaxially nested with described outer input shaft, on described interior input shaft and described outer input shaft, is provided with each fast driving gear; Tween drive shaft with described input shaft and described output shaft are arranged in parallel, is provided with the multiple driven gears that engage with described driving gear on described tween drive shaft, be also provided with intermediate gear on described tween drive shaft; Optionally switch the synchro of moment output; With described input shaft and the coaxially arranged transition axis of described output shaft, described transition axis one end is provided with the transition gear engaging with described intermediate gear, the other end connects the first sun and planet gear, and the moment of torsion of described transition gear transmission is exported by output shaft through described the first sun and planet gear converter speed ratio or after becoming velocity reversal; Also comprise motor, the rotating shaft of described motor connects the second sun and planet gear, between described the second sun and planet gear and described tween drive shaft, is provided with electric motor clutch.
Preferably, described the first sun and planet gear is La Weina sun and planet gear, small sun gear wherein and described transition axis are rigidly connected, the rotation of large sun wheel is subject to the first drg control, planet gear mechanism clutch is set after the pinion carrier of short satellite gear and long satellite gear is rigidly connected and between described transition axis and is subject to second brake control.
Preferably, described the second sun and planet gear is single planetary gear mechanism, and wherein the rotating shaft of sun wheel and described motor is rigidly connected, and pinion carrier is connected with described electric motor clutch.
The utility model is directly passed to tween drive shaft by the moment of torsion of motor through the second sun and planet gear, pass to output shaft through transition axis, the first sun and planet gear again, instead of passing to first clutch or second clutch housing, this is conducive to improve speed of response and makes up the moment of torsion output loss that the first sun and planet gear causes due to converter speed ratio.The utility model becomes velocity reversal by the first sun and planet gear, has saved reverse gear shaft and reverse idler gear, makes structure further compact.
Further, the second sun and planet gear in the utility model adopts the connection mode that increases moment of torsion, guarantees car load power output performance.
Brief description of the drawings
Next in connection with accompanying drawing, specific embodiment of the utility model is described in further detail, wherein:
Fig. 1 is the vertical pair clutch gearbox transmission structures schematic diagrams of putting of the hybrid power of embodiment of the present utility model.
Description of symbols in upper figure: 1, outer input shaft, 2, interior input shaft, 3, tween drive shaft, 4, transition axis, 5, output shaft, 6, the first sun and planet gear, 7, the second sun and planet gear, 8, machine shaft, 11, the first fast driving gear, 12, the second fast driving gear, 23, the 3rd fast driving gear, 31, the first fast driven gear, 32, the second fast driven gear, 33, the 3rd fast driven gear, 30, intermediate gear, 40, transition gear, 62a, small sun gear, 62b, large sun wheel, 66a, short satellite gear, 66b, long satellite gear, 68, gear ring, 69, pinion carrier, 71, motor soldered tooth, 72, the second sun and planet gear sun wheel, 79, the second sun and planet gear pinion carrier, the first synchro SC1, the second synchro SC2, electric motor clutch K2, first clutch C1, second clutch C2, the first drg B1, second brake B2, planet gear mechanism clutch K1, motor EM,
Detailed description of the invention
With reference to figure 1, first clutch C1 is connected with interior input shaft 2, second clutch C2 is connected with outer input shaft 1, by the open and close controlling of power-transfer clutch C1 and C2, can selectively driving engine (not showing in Fig. 1) moment of torsion be delivered to outer input shaft 1 or interior input shaft 2.From left to right, on (Fig. 1 shows, is right near driving engine one side for a left side, away from driving engine one side) outer input shaft 1, arranging successively the first fast driving gear 11, the second fast driving gear (reverse driving gear) 12; On interior input shaft 2, arranging the 3rd fast driving gear 23.Like this, from whole input shaft assembly 1,2, odd number shelves driving gear is disposed on outer input shaft 1, and even number shelves and reverse driving gear are disposed on interior input shaft 2.From left to right (Fig. 1 shows, is a left side, is the right side away from driving engine one side near driving engine one side), arrangement of gears order is followed successively by: the first fast driving gear 11, the second fast driving gear 12, the 3rd fast driving gear 13.Wherein, the first fast driving gear 11, the second fast driving gear 12 are rigidly connected outside on input shaft 1, the 3rd fast driving gear 13 by bearings on interior input shaft 2.And in the 3rd fast driving gear 13 rear ends, the second synchro SC2 is installed, this device is rigidly attached on interior input shaft 2, can be optionally by fast the transmission of power to the three on interior input shaft 2 driving gear 13 or transition axis 4.
Transition axis 4 and input shaft 1 coaxial line layout, transition axis 4 one end rigid connectings are connected to output gear 40.
Tween drive shaft 3 and input shaft 1,2 are arranged in parallel, and on tween drive shaft 3, (being the right side for a left side, away from driving engine one side near driving engine one side) is provided with the first fast driven gear 31, the second fast driven gear 32, the 3rd fast driven gear 33, intermediate gear 30 from left to right.Wherein, the first fast driven gear 31, the second fast driven gear 32 are by bearings tween drive shaft 3.The 3rd fast driven gear 33 and intermediate gear 30 are rigidly attached on tween drive shaft.Between the first fast driven gear 31, the second fast driven gear 32, arranged the first synchro SC1, the first synchro SC1 and tween drive shaft are rigidly connected.This synchromesh gear can optionally optionally be delivered to the power of the first fast driven gear 31, the second fast driven gear 32 on tween drive shaft 3.
The first sun and planet gear 6 is La Weina (Ravigneaux) sun and planet gear, coaxially arranged with input shaft 1,2, at transition axis 4 other ends, small sun gear 62a and transition axis 4 are rigidly connected, large sun wheel 62b rotates and controlled by the first drg B1, the pinion carrier of short satellite gear 66a and long satellite gear 66b is rigidly connected and becomes pinion carrier 69, and pinion carrier 69 is rotated and controlled by planet gear mechanism clutch K1, second brake B2.
By controlling, drg B1 and B2, planet gear mechanism clutch K1 are closed can obtain 2 different forward speed ratios and 1 speed ratio that falls back from opening.And then coordinate with 4 speed ratios of the first synchro SC1, SC2 control, obtain multiple gear forward speed ratios and the speed ratio that falls back.
The second sun and planet gear 7 adopts single planetary gear mechanism, gear ring is fixed, sun wheel 72 is rigidly connected with machine shaft 8, pinion carrier 79 is rigidly connected with motor soldered tooth 71, between the pinion carrier 79 of the second sun and planet gear 7 and tween drive shaft 3, electric motor clutch K2 is set, engage electric motor clutch K2 and the power of motor EM output can be passed to transition axis 4 by gear pair intermediate gear 30 and transition gear 40, form hybrid power output.
Power transmission line explanation:
1 grade of power transmission line: the first synchro SC1 and the first fast driven gear 31 combinations, the first drg B1 closure, first clutch C1 closure, engine torque passes to outer input shaft 1 by first clutch C1, via the first fast driving and driven gear 11,31 and the first synchro SC1, transfer torque to tween drive shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, again through small sun gear 62a, short satellite gear 66a, long satellite gear 66b and gear ring 68 by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
2 grades of power transmission lines: the second synchro SC2 and the 3rd fast driving gear 23 combinations, the first drg B1 closure, second clutch C2 closure, engine torque passes to interior input shaft 2 by power-transfer clutch C2, via the second synchro SC2, the 3rd fast driving and driven gear 23,33, transfer torque to tween drive shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, again through small sun gear 62a, short satellite gear 66a, long satellite gear 66b and gear ring 68 by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
3 grades of power transmission lines: the first synchro SC1 and the first fast driving gear 31 combinations, planet gear mechanism clutch K1 closure, first clutch C1 closure, engine torque passes to outer input shaft 1 by first clutch C1, main via the first speed, driven gear 11, 31 and the first synchro SC1, transfer torque to tween drive shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, now small sun gear 62a and pinion carrier 69 are rigidly connected, whole sun and planet gear 6 directly by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
4 grades of power transmission lines: the second synchro SC2 and the 3rd fast driven gear 23 combinations, planet gear mechanism clutch K1 closure, second clutch C2 closure, engine torque passes to interior input shaft 2 by second clutch C2, via the second synchro SC2, the 3rd speed is main, driven gear 23, 33, transfer torque to tween drive shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, now small sun gear 62a and pinion carrier 69 are rigidly connected, whole sun and planet gear 6 directly by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
5 grades of power transmission lines: the first synchro SC1 and the second fast driven gear 32 combinations, the first drg B1 closure, first clutch C1 closure, engine torque passes to outer input shaft 1 by first clutch C1, via the second fast driving and driven gear 12,32 and the second synchro SC2, transfer torque to tween drive shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, again through small sun gear 62a, short satellite gear 66a, long satellite gear 66b and gear ring 68 by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
6 grades of power transmission lines: the second synchro SC2 and transition gear 40 combinations, planet gear mechanism clutch K1 closure, second clutch C2 closure, engine torque passes to interior input shaft 2 by power-transfer clutch C2, through the second synchro SC2, transition axis 4, now small sun gear 62a and pinion carrier 69 are rigidly connected, whole sun and planet gear 6 directly by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
7 grades of power transmission lines: the first synchro SC1 and the second fast driven gear 32 combinations, planet gear mechanism clutch K1 closure, first clutch C1 closure, engine torque passes to outer input shaft 1 by first clutch C1, main via the second speed, driven gear 12, 32 and the second synchro SC2, transfer torque to tween drive shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, now small sun gear 62a and pinion carrier 69 are rigidly connected, whole sun and planet gear 6 directly by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
Reverse gear power transmission line: the second synchro SC2 and transition gear 40 combinations, second brake B2 closure, second clutch C2 closure, engine torque passes to interior input shaft 2 by second clutch C2, through the second synchro SC2, transition axis 4, then through small sun gear 62a, short satellite gear 66a, long satellite gear 66b and gear ring 68 by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
Vehicle utilize motor EM to realize the start and stop of vehicle: when need to start, engage electric motor clutch K2, pass to tween drive shaft 3 by EM motor power outputting power by single planetary gear mechanism 7, electric motor clutch K2, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, then export to output shaft 5 through sun and planet gear 6, and then drive car load to start.When vehicle will stop, engaging electric motor clutch K2, the access of motor EM power, engine stoping operation, pure motor EM drives car load to travel, ramp to stop.
Pure electric drive: engage electric motor clutch K2, engine stop work, disconnect double-clutch C1, C2, the power of being exported by motor EM is passed to tween drive shaft 3 by single planetary gear mechanism 7, electric motor clutch K2, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, then export to output shaft 5 through sun and planet gear 6, and then drive car load to travel, realize motor EM individual drive car load and travel.
Combination drive: engine work, a certain gear work in this driving device place, power outputs to transition axis 4; Electric motor clutch K2 is in engagement state, and the power of motor EM output is passed to tween drive shaft 3 by single planetary gear mechanism 7, electric motor clutch K2, then by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4; The power of the power of driving engine output and motor EM output is exported to output shaft 5 by sun and planet gear 7 jointly, and then drives car load to travel.
Smooth-ride generating: vehicle is in the time of combination drive smooth-ride, and when engine output power is greater than the required propulsive effort of Vehicle Driving Cycle, motor EM stops power output, as electrical generator, is driven generating.
Visible, the utility model is directly passed to tween drive shaft 3 by the moment of torsion of motor EM through the second sun and planet gear 7, pass to output shaft 5 through transition axis 4, the first sun and planet gear 6 again, instead of passing to first clutch or second clutch housing, this is conducive to improve speed of response and makes up the moment of torsion output loss that the first sun and planet gear 6 causes due to converter speed ratio.The utility model becomes velocity reversal by the first sun and planet gear 6, has saved reverse gear shaft and reverse idler gear, makes structure further compact.
And the second sun and planet gear 7 in the utility model adopts the connection mode that increases moment of torsion, guarantees car load power output performance.
Power-transfer clutch, synchro, drg course of action when table 1 has shown to realize each gear.
Table 1
Gearshift procedure casehistory:
One grade is changed second gear process: dual-clutch transmission is in one grade, and the first synchro SC1 and the first fast driven gear 31 be in conjunction with, the first drg B1 closure, first clutch C1 closure, and second clutch C2 opens; Dual-clutch transmission control system (not showing in accompanying drawing 1) is sent one grade and is changed second gear instruction, gear-shifting actuating mechanism continues closed by the second synchro SC2 and the 3rd fast driving gear 23 combinations, the first drg B1 in advance, now second clutch C2 is still in open mode, i.e. transferring power not of second clutch C2 and interior input shaft 2; Along with gearshift procedure continues, first clutch C1 opens gradually, and meanwhile, second clutch C2 is closed gradually, and this process there will not be torque break; First clutch C1 opens completely, after the complete closure of second clutch C2, the first synchro SC1 throws off the combination of the first fast driven gear 31, finishes gearshift procedure.Engine torque passes to interior input shaft 2 by second clutch C2, via the 3rd fast driving and driven gear 23,33 and the second synchro SC2, transfer torque to tween drive shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, again through small sun gear 62a, short satellite gear 66a, long satellite gear 66b and gear ring 68 by transmission of power to output shaft 5, and finally by output shaft 5 outputting powers.
The utility model adopt the two couples of synchro SC1 and SC2, with two drg B1 and B2, single clutch K1, a La Weina (Ravigneaux) planet row 6, realize flexibly 7 forward gears and 1 reverse gear, speed ratio width is larger, be conducive to dynamic property and economy, part still less, compacter, be more conducive to lightweight.
The utility model adopts two drg B1 and B2, and a single clutch K1, coordinates to eliminate the speed discrepancy between change speed gear box inner member with two synchros, by reducing the working strength of such friction element, increases the service life;
The utility model utilizes motor EM to realize the start and stop of vehicle, avoids the idling work interval of driving engine; Can realize pure electric drive, motor EM independent drive vehicles travels; Can realize combination drive, motor EM and driving engine drive Vehicle Driving Cycle jointly; Can realize smooth-ride generating, vehicle is in the time of combination drive smooth-ride, and when engine output power is greater than the required propulsive effort of Vehicle Driving Cycle, motor EM stops power output, as electrical generator, is driven generating.
Although the utility model is described in conjunction with above embodiment, but the utility model is not defined to above-described embodiment, and be only subject to the restriction of claim, those of ordinary skill in the art can easily modify to it and change, but do not leave essence design of the present utility model and scope.
Claims (3)
1. the vertical pair clutch gearbox drivings device of putting of hybrid power, comprising:
First clutch and second clutch;
The interior input shaft being connected with described first clutch and the outer input shaft being connected with described second clutch, described interior input shaft is coaxially nested with described outer input shaft, on described interior input shaft and described outer input shaft, is provided with each fast driving gear;
Tween drive shaft with described input shaft and output shaft are arranged in parallel, is provided with the multiple driven gears that engage with described driving gear on described tween drive shaft, be also provided with intermediate gear on described tween drive shaft;
Optionally switch the synchro of moment output;
With described input shaft and the coaxially arranged transition axis of described output shaft, described transition axis one end is provided with the transition gear engaging with described intermediate gear, the other end connects the first sun and planet gear, and the moment of torsion of described transition gear transmission is exported by output shaft through described the first sun and planet gear converter speed ratio or after becoming velocity reversal;
It is characterized in that, also comprise motor, the rotating shaft of described motor connects the second sun and planet gear, between described the second sun and planet gear and described tween drive shaft, is provided with electric motor clutch.
2. the vertical pair clutch gearbox drivings device of putting of hybrid power according to claim 1, it is characterized in that, described the first sun and planet gear is La Weina sun and planet gear, small sun gear wherein and described transition axis are rigidly connected, the rotation of large sun wheel is subject to the first drg control, planet gear mechanism clutch is set after the pinion carrier of short satellite gear and long satellite gear is rigidly connected and between described transition axis and is subject to second brake control.
3. the vertical pair clutch gearbox drivings device of putting of hybrid power according to claim 1, it is characterized in that, described the second sun and planet gear is single planetary gear mechanism, and wherein the rotating shaft of sun wheel and described motor is rigidly connected, and pinion carrier is connected with described electric motor clutch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420258449.3U CN203902248U (en) | 2014-05-19 | 2014-05-19 | Longitudinal hybrid dual-clutch transmission actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420258449.3U CN203902248U (en) | 2014-05-19 | 2014-05-19 | Longitudinal hybrid dual-clutch transmission actuator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203902248U true CN203902248U (en) | 2014-10-29 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420258449.3U Expired - Fee Related CN203902248U (en) | 2014-05-19 | 2014-05-19 | Longitudinal hybrid dual-clutch transmission actuator |
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| Country | Link |
|---|---|
| CN (1) | CN203902248U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106183780A (en) * | 2016-08-30 | 2016-12-07 | 上海交通大学 | The coaxial coupling drive system of dual planetary gear system bi-motor |
| CN109505939A (en) * | 2018-12-28 | 2019-03-22 | 东风商用车有限公司 | Hybrid power gearbox |
| CN109689411A (en) * | 2016-09-07 | 2019-04-26 | 舍弗勒技术股份两合公司 | Hybrid powertrain with intermediate gear |
-
2014
- 2014-05-19 CN CN201420258449.3U patent/CN203902248U/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106183780A (en) * | 2016-08-30 | 2016-12-07 | 上海交通大学 | The coaxial coupling drive system of dual planetary gear system bi-motor |
| CN106183780B (en) * | 2016-08-30 | 2023-07-25 | 上海交通大学 | Double-planetary gear train double-motor coaxial coupling driving system |
| CN109689411A (en) * | 2016-09-07 | 2019-04-26 | 舍弗勒技术股份两合公司 | Hybrid powertrain with intermediate gear |
| CN109689411B (en) * | 2016-09-07 | 2022-03-29 | 舍弗勒技术股份两合公司 | Hybrid powertrain with intermediate gear |
| CN109505939A (en) * | 2018-12-28 | 2019-03-22 | 东风商用车有限公司 | Hybrid power gearbox |
| CN109505939B (en) * | 2018-12-28 | 2024-03-19 | 东风商用车有限公司 | Hybrid power gearbox |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 230601 Anhui Province, Hefei City Industrial Park, the Peach Blossom Road No. 669 Patentee after: Anhui Jianghuai Automobile Group Limited by Share Ltd Address before: 230601 Anhui Province, Hefei City Industrial Park, the Peach Blossom Road No. 669 Patentee before: Anhui Jianghuai Automobile Co., Ltd. |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20141029 Termination date: 20190519 |