CN203880024U - Hybrid power longitudinal double-clutch gearbox transmission device - Google Patents
Hybrid power longitudinal double-clutch gearbox transmission device Download PDFInfo
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- CN203880024U CN203880024U CN201420257069.8U CN201420257069U CN203880024U CN 203880024 U CN203880024 U CN 203880024U CN 201420257069 U CN201420257069 U CN 201420257069U CN 203880024 U CN203880024 U CN 203880024U
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- 238000000034 method Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 5
- 230000008859 change Effects 0.000 description 2
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Abstract
The utility model provides a hybrid power longitudinal double-clutch gearbox transmission device. The torque of a motor is directly transmitted to a middle shaft through a second planet gear mechanism and then transmitted to an output shaft instead of a first clutch or a second clutch shell through a transmission shaft and a first planet gear mechanism. By the arrangement, response speed can be increased favorably and torque output loss, caused by gear ratio, of the first planet gear mechanism can be compensated.
Description
Technical field
The utility model relates to automotive transmission field.
Background technique
The general vertical double clutch transmissions of putting is by two groups of coaxial nested or clutches of being arranged in parallel, coaxially, two of inside and outside nested arrangement input shafts, a jack shaft being arranged in parallel, an output shaft coaxially arranged with input shaft, is arranged in a plurality of synchromesh gears on output shaft, a plurality of selector fork composition.Speed changer is strange, even number gear input gear is arranged on two input shafts, and switching and different synchronizer by two clutches move, and via different output shafts, realize torque conversion and output.Thereby in prior art, utilize planetary gears to change speed ratio and increase the gear quantity that can realize, while adopting mixed power, Motor torque is realized with the independent of engine power or is mixed output by first, second clutch housing, now Motor torque output can be subject to bang path, planetary gears changes the adverse effect of speed ratio, and then affects car load power output performance.
Model utility content
The purpose of this utility model is to provide the more steadily vertical pair clutch gearbox transmission devices of putting of reliable mixed power of a kind of power output, and embodiment of the present utility model provides following technological scheme for this reason:
The vertical pair clutch gearbox transmission devices of putting of mixed 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; The jack shaft and the reverse gear shaft that are arranged in parallel with described input shaft and described output shaft, on described jack shaft, be provided with a plurality of driven gears with described driving gear engagement, on described jack shaft, be also provided with intermediate gear, on described reverse gear shaft, be provided with the idle pulley that reverses gear with a described driving gear engagement; Optionally switch the synchronizer 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 with described intermediate gear engagement, the other end connects the first planetary gears, and the moment of torsion of described transition gear transmission is exported by output shaft after described the first planetary gears gear ratio; Also comprise motor, the rotating shaft of described motor connects the second planetary gears, between described the second planetary gears and described jack shaft, is provided with motor synchronizer.
Preferably, described the first planetary gears is La Weina planetary gears, small sun gear wherein and described transition axis are rigidly connected, the rotation of large sun gear is controlled by the first break, planet gear mechanism clutch is set after the planet carrier of short planet wheel and long planet wheel is rigidly connected and between described transition axis and controlled by second brake.
Preferably, the planet carrier of described short planet wheel and described long planet wheel is controlled by overrunning clutch after being rigidly connected.
Preferably, described the second planetary gears is single planetary gear mechanism, and wherein the rotating shaft of sun gear and described motor is rigidly connected, and planet carrier is connected with described motor synchronizer.
The utility model is directly passed to jack shaft by the moment of torsion of motor through the second planetary gears, through transition axis, the first planetary gears, pass to output shaft again, rather than 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 planetary gears causes due to gear ratio.
Further, the second planetary gears in the utility model adopts the Placement that increases moment of torsion, guarantees car load power output performance.
Accompanying drawing explanation
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 diagram of putting of embodiment's of the present utility model mixed power.
Description of symbols in upper figure: 1, interior input shaft, 2, outer input shaft, 3, jack shaft, 4, transition axis, 5, reverse gear shaft, 6, output shaft, 7, the first planetary gears, 8, the second planetary gears, 9, machine shaft, 11, the first fast driving gear, 22, the second fast driving gear (driving gear reverses 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, 50, the idle pulley that reverses gear, 72a, small sun gear, 72b, large sun gear, 76a, short planet wheel, 76b, long planet wheel, 78, gear ring, 79, planet carrier, 81, motor soldered tooth, 82, the second planetary gears sun gear, 89, the second planetary gears planet carrier, the first synchronizer SC1, the second synchronizer SC2, first clutch C1, second clutch C2, the first break B1, second brake B2, planet gear mechanism clutch K1, motor synchronizer SC3, overrunning clutch F, motor EM.
Embodiment
With reference to figure 1, first clutch C1 is connected with interior input shaft 1, second clutch C2 is connected with outer input shaft 2, thereby interior input shaft 1 and coaxial nested can the relatively rotating of outer input shaft 2, by the open and close controlling of clutch C1 and C2, can selectively motor (not showing in Fig. 1) moment of torsion be delivered to interior input shaft 1 or outer input shaft 2.On interior input shaft 1, be provided with the first fast driving gear 11; On outer input shaft 2, (Fig. 1 shows that be the right side near motor one side for a left side, away from motor one side) setting gradually the fast driving gear 22 of the 3rd fast driving gear 23, second from left to right, wherein, the second fast driving gear 22 is used as the driving gear that reverses gear simultaneously.Like this, from whole input shaft assembly 1,2, odd number gear driving gear is disposed on interior input shaft 1, and even number gear and the driving gear that reverses gear are disposed on outer input shaft 2.From left to right (Fig. 1 shows that be the right side near motor one side for a left side, away from motor one side), arrangement of gears is sequentially followed successively by: the 3rd fast driving gear the 23, second fast driving gear (driving gear reverses gear) 22 first fast driving gears 11.Wherein, the 3rd fast driving gear the 23, second fast driving gear (driving gear reverses gear) 22 is rigidly connected outside on input shaft 2, the first fast driving gear 11 by bearings on interior input shaft 1.And in the first fast driving gear 11 rear ends, the first synchronizer SC1 is installed, this device is rigidly attached on interior input shaft 1, can be optionally by the fast driving gear 11 of the transmission of power to the first on interior input shaft 1 or transition axis 4.
Transition axis 4 is coaxially arranged with input shaft 1, and transition axis 4 one end rigid connectings are connected to transition gear 40.
Jack shaft 3 and two input shafts 1,2 are arranged in parallel, and on jack shaft 3, (near motor one side, for a left side, away from motor one side, being the right side) is provided with the fast driven gear 31 of the fast driven gear 32, first of the 3rd fast driven gear 33, second, intermediate gear 30 from left to right.Wherein, the fast driven gear 32 of the 3rd fast driven gear 33, second is by bearings jack shaft 3.The first fast driven gear 31 and intermediate gear 30 are rigidly attached on jack shaft.Between the fast driven gear 32 of the 3rd fast driven gear 33, second, arranged the second synchronizer SC2, the second synchronizer SC2 and jack shaft 3 are rigidly connected, this synchromesh gear can be optionally by the transmission of power of the 3rd fast driven gear the 33, second fast driven gear 32 to jack shaft 3.
Motor synchronizer SC3 and jack shaft are rigidly connected.
Reverse gear shaft 5 and two input shafts 1,2 are arranged in parallel, and the idle pulley 50 that reverses gear is installed on reverse gear shaft 5, and the idle pulley 50 that reverses gear is rigidly attached on reverse gear shaft 5.
The first planetary gears 7 is La Weina (Ravigneaux) planetary gears, coaxially arranged with input shaft 1,2.
At transition axis 4 the other ends, small sun gear 72a and transition axis 4 are rigidly connected, large sun gear 72b rotates and controlled by the first break B1, the planet carrier of short planet wheel 76a and long planet wheel 76b is rigidly connected and becomes planet carrier 79, planet carrier 79 rotates and controlled by planet gear mechanism clutch K1, second brake B2, and overrunning clutch F limits rotating backward of planet carrier 79.By controlling the first break B1 and second brake B2, planet gear mechanism clutch K1 closure and opening, obtain 3 different speed ratios.And then coordinate with 4 speed ratios (comprise and reversing gear) of synchromesh gear SC1, SC2 control, obtain a plurality of gear speed ratios.
The second planetary gears 8 adopts single planetary gear mechanism, gear ring is fixed, sun gear 82 is rigidly connected with machine shaft 9, planet carrier 89 is rigidly connected with motor soldered tooth 81, between the planet carrier of motor planetary gear mechanism 8 and jack shaft 3, motor synchronizer SC3 is set, engage motor synchronizer SC3 and the power of motor EM output can be passed to excess axle 4 by gear pair intermediate gear 30 and transition gear 40, form mixed power output.Visible, the moment of torsion of motor EM is not to pass to first clutch C1 or second clutch C2 housing, and this is conducive to improve speed of response and makes up the moment of torsion output loss that the first planetary gears 7 causes due to gear ratio.And the second planetary gears 8 adopts the Placement that increases moment of torsion, guarantees car load power output performance.
Power transmission line explanation:
1 gear power transmission line: the first synchronizer SC1 and the first fast driving gear 11 combinations, second brake B2 is closed, first clutch C1 is closed, Engine torque passes to interior input shaft 1 by first clutch C1, via the first fast driving and driven gear 11,31 and the first synchromesh gear SC1, transfer torque to jack 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 72a, short planet wheel 76a, long planet wheel 76b and gear ring 78 by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
2 gear power transmission lines: the second synchronizer SC2 and the second fast driven gear 33 combinations, second brake B2 is closed, second clutch C2 is closed, Engine torque passes to outer input shaft 2 by second clutch C2, via the second fast driving and driven gear 22,33 and the second synchronizer SC2, transfer torque to jack 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 72a, short planet wheel 76a, long planet wheel 76b and gear ring 78 by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
3 gear power transmission lines: the first synchronizer SC1 and the first fast driving gear 31 combinations, the first break B1 is closed, first clutch C1 is closed, Engine torque passes to interior input shaft 1 by first clutch C1, via the first fast driving and driven gear 11,31 and the first synchronizer SC1, transfer torque to jack 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 72a, short planet wheel 76a, long planet wheel 76b and gear ring 78 by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
4 gear power transmission lines: the second synchronizer SC2 and the 3rd fast driven gear 33 combinations, the first break B1 is closed, second clutch C2 is closed, Engine torque passes to outer input shaft 2 by second clutch C2, via the 3rd fast driving and driven gear 23,33 and the second synchronizer SC2, transfer torque to jack 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 72a, short planet wheel 76a, long planet wheel 76b and gear ring 78 by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
5 gear power transmission lines: the first synchronizer SC1 and transition gear 40 combinations, planetary gears second brake B2 is closed, first clutch C1 is closed, Engine torque passes to interior input shaft 1 by first clutch C1, through the first synchronizer SC1, transition axis 4, now small sun gear 72a and planet carrier 79 are rigidly connected, whole planetary gears 7 directly by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
6 gear power transmission lines: synchromesh gear SC2 and the second fast driven gear 33 combinations, planet gear mechanism clutch K1, clutch C2 is closed, Engine torque passes to outer input shaft 2 by clutch C2, via the second fast driving and driven gear 22,33 and synchromesh gear SC2, transfer torque to jack shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, now small sun gear 72a and planet carrier 79 are rigidly connected, whole planetary gears 7 directly by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
7 gear power transmission lines: the first synchronizer SC1 and transition gear 40 combinations, planetary gears the first break B1 is closed, first clutch C1 is closed, Engine torque passes to interior input shaft 1 by first clutch C1, through the first synchronizer SC1, transition axis 4, now small sun gear 72a and planet carrier 79 are rigidly connected, whole planetary gears 7 directly by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
Power transmission line reverses gear: the second synchronizer SC2 and the second fast driven gear 32 combinations, second brake B2 is closed, second clutch C2 is closed, Engine torque passes to outer input shaft 2 by second clutch C2, via the second fast driving gear 22, idle pulley 50 reverses gear, the second fast driven gear 32 and the second synchronizer SC2, transfer torque to jack 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 72a, short planet wheel 76a, long planet wheel 76b and gear ring 78 by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
Vehicle utilize motor EM to realize the start and stop of vehicle: when need to start, engage motor synchronizer SC3, by motor EM outputting power, by single planetary gear mechanism 8, motor synchronizer SC3, pass to jack shaft 3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, then through planetary gears 7, export to output shaft 6, and then drive car load to start.When vehicle will stop, engaging motor synchronizer SC3, the access of motor EM power, engine stoping operation, pure motor EM drives car load to travel, ramp to stop.
Pure electric drive: engage motor synchronizer SC3, engine stop work, disconnect double clutch C1, C2, the power of being exported by motor EM is passed to jack shaft 3 by single planetary gear mechanism 8, motor synchronizer SC3, by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4 again, then through planetary gears 7, export to output shaft 6, and then drive car load to travel, realize motor EM drive car load and travel.
Combination drive: engine work, a certain gear work in this transmission device place, power outputs to transition axis 4; Motor synchronizer SC3 is in jointing state, and the power of motor EM output is passed to jack shaft 3 by single planetary gear mechanism 8, motor synchronizer SC3, then by intermediate gear 30 and transition gear 40, moment of torsion is passed to transition axis 4; The power of the power of motor output and motor EM output is exported to output shaft 6 by planetary gears 7 jointly, and then drives car load to travel.
Smooth-ride generating: vehicle is when combination drive smooth-ride, and when engine output power is greater than the required driving force of Vehicle Driving Cycle, motor EM stops power output, as generator, driven generating.
Clutch, synchronizer, break course of action when table 1 has shown to realize each gear.
Table 1
Shift process illustrates:
The one gear process that shifts into second: dual-clutch transmission is in a gear, the first synchronizer SC1 and the first fast driven gear 31 are closed in conjunction with, second brake B2, and first clutch C1 is closed, and second clutch C2 opens; Dual-clutch transmission control system (in accompanying drawing 1 do not show) is sent the gear instruction that shifts into second, gear shifting actuating mechanism is closed in conjunction with, the first break B1 by the second synchronizer SC2 and the 3rd fast driven gear 33 in advance, now second clutch C2 is still in open mode, i.e. second clutch C2 and outer input shaft 2 transferring power not; Along with shift process 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 synchronizer SC1 throws off the combination of the first fast driven gear 31, finishes shift process.Engine torque passes to outer input shaft 2 by second clutch C2, via the 3rd fast driving and driven gear 23,33 and the second synchronizer SC2, transfer torque to jack 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 72a, short planet wheel 76a, long planet wheel 76b and gear ring by transmission of power to output shaft 6, and finally by output shaft 6 outputting powers.
The utility model adopt two couples of synchronizer SC1 and SC2, with two break B1 and B2, planet gear mechanism clutch K1, a La Weina (Ravigneaux) planetary gears 7, realizing flexibly 7 forward gears and 1 reverses gear, speed ratio width is larger, is conducive to power character and Economy; Part still less, compacter, is more conducive to lightweight.
The utility model adopts two break B1 and B2, and a planet gear mechanism clutch K1, coordinates to eliminate the speed discrepancy between gearbox inner member with two synchronizers, 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, and the idling work of avoiding motor is interval.
The utility model can be realized pure electric drive, and motor EM independent drive vehicles travels; Combination drive, motor EM and motor drive Vehicle Driving Cycle jointly; Smooth-ride generating, vehicle is when combination drive smooth-ride, and when engine output power is greater than the required driving force of Vehicle Driving Cycle, motor EM stops power output, as generator, 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 skills can easily modify to it and change, but do not leave essence design of the present utility model and scope.
Claims (4)
1. mixed power is indulged and is put two clutch gearbox transmission devices, 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;
The jack shaft and the reverse gear shaft that are arranged in parallel with described input shaft and output shaft, on described jack shaft, be provided with a plurality of driven gears with described driving gear engagement, on described jack shaft, be also provided with intermediate gear, on described reverse gear shaft, be provided with the idle pulley that reverses gear with a described driving gear engagement;
Optionally switch the synchronizer 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 with described intermediate gear engagement, the other end connects the first planetary gears, and the moment of torsion of described transition gear transmission is exported by output shaft after described the first planetary gears gear ratio;
It is characterized in that, also comprise motor, the rotating shaft of described motor connects the second planetary gears, between described the second planetary gears and described jack shaft, is provided with motor synchronizer.
2. mixed power according to claim 1 is indulged and is put two clutch gearbox transmission devices, it is characterized in that, described the first planetary gears is La Weina planetary gears, small sun gear wherein and described transition axis are rigidly connected, the rotation of large sun gear is controlled by the first break, planet gear mechanism clutch is set after the planet carrier of short planet wheel and long planet wheel is rigidly connected and between described transition axis and controlled by second brake.
3. the vertical pair clutch gearbox transmission devices of putting of mixed power according to claim 2, is characterized in that, after the planet carrier of described short planet wheel and described long planet wheel is rigidly connected, controlled by overrunning clutch.
4. mixed power according to claim 1 is indulged and is put two clutch gearbox transmission devices, it is characterized in that, described the second planetary gears is single planetary gear mechanism, and wherein the rotating shaft of sun gear and described motor is rigidly connected, and planet carrier is connected with described motor synchronizer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420257069.8U CN203880024U (en) | 2014-05-19 | 2014-05-19 | Hybrid power longitudinal double-clutch gearbox transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420257069.8U CN203880024U (en) | 2014-05-19 | 2014-05-19 | Hybrid power longitudinal double-clutch gearbox transmission device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203880024U true CN203880024U (en) | 2014-10-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420257069.8U Expired - Fee Related CN203880024U (en) | 2014-05-19 | 2014-05-19 | Hybrid power longitudinal double-clutch gearbox transmission device |
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| Country | Link |
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| CN (1) | CN203880024U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115111331A (en) * | 2022-01-27 | 2022-09-27 | 长城汽车股份有限公司 | Transmission, vehicle power device and vehicle |
| CN117207767A (en) * | 2023-10-30 | 2023-12-12 | 哈尔滨东安汽车发动机制造有限公司 | Transmission for longitudinal front-drive hybrid electric vehicle and working method thereof |
-
2014
- 2014-05-19 CN CN201420257069.8U patent/CN203880024U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115111331A (en) * | 2022-01-27 | 2022-09-27 | 长城汽车股份有限公司 | Transmission, vehicle power device and vehicle |
| CN117207767A (en) * | 2023-10-30 | 2023-12-12 | 哈尔滨东安汽车发动机制造有限公司 | Transmission for longitudinal front-drive hybrid electric vehicle and working method thereof |
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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: 20141015 Termination date: 20190519 |