CN203822968U - Hybrid longitudinal dual-clutch transmission drive device - Google Patents
Hybrid longitudinal dual-clutch transmission drive device Download PDFInfo
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- CN203822968U CN203822968U CN201420259288.XU CN201420259288U CN203822968U CN 203822968 U CN203822968 U CN 203822968U CN 201420259288 U CN201420259288 U CN 201420259288U CN 203822968 U CN203822968 U CN 203822968U
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- gear
- clutch
- shaft
- input shaft
- planetary gears
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Abstract
The utility model provides a hybrid longitudinal dual-clutch transmission drive device. Torque of a motor is transmitted to an intermediate shaft directly through a planetary gear mechanism, and then transmitted to an output shaft through a transition shaft and a first planetary gear mechanism, rather than a first clutch housing or a second clutch housing, which is favorable for increasing the response speed and making up for a torque output loss of the first planetary gear mechanism due to gear ratio.
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 the multiple synchromesh gears on output shaft, multiple reverse shift fork composition.Speed changer is strange, even number shelves input gear is arranged on two input shafts, by switching and the action of different synchronizer of two clutches, realizes torque conversion and output via different output shafts.Thereby in prior art, utilize planetary gears to change speed ratio and increase the numbers of gear steps 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 a kind 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; Jack 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 jack shaft, be also provided with intermediate gear on described jack shaft; 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 engaging with described intermediate gear, the other end connects the first planetary gears, and the moment of torsion of described transition gear transmission is exported by output shaft through described the first planetary gears gear ratio or after becoming velocity attitude; 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 subject to the first break control, 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 is subject to second brake control.
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, pass to output shaft through transition axis, the first planetary gears 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 planetary gears causes due to gear ratio.The utility model becomes velocity attitude by the first planetary gears, has saved reverse gear shaft and reverse idler gear, makes structure further compact.
Further, the second planetary gears in the utility model adopts the Placement 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 diagram of putting of embodiment's of the present utility model mixed power.
Description of symbols in upper figure: 1, outer input shaft, 2, interior input shaft, 3, jack shaft, 4, transition axis, 5, output shaft, 6, the first planetary gears, 7, the second planetary gears, 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 gear, 66a, short planet wheel, 66b, long planet wheel, 68, gear ring, 69, planet carrier, 71, motor soldered tooth, 72, the second planetary gears sun gear, 79, the second planetary gears planet carrier, the first synchronizer SC1, the second synchronizer SC2, motor synchronizer SC3, first clutch C1, second clutch C2, the first break B1, second brake B2, planet gear mechanism clutch K1, motor EM,
Embodiment
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 clutch C1 and C2, can selectively motor (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 motor one side for a left side, away from motor 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 motor one side near motor 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 synchronizer 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.
Jack shaft 3 and input shaft 1,2 are arranged in parallel, and on jack shaft 3, (being the right side for a left side, away from motor one side near motor 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 jack shaft 3.The 3rd fast driven gear 33 and intermediate gear 30 are rigidly attached on jack shaft.Between the first fast driven gear 31, the second fast driven gear 32, arranged the first synchronizer SC1, the first synchronizer SC1 and jack 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 jack shaft 3.
The first planetary gears 6 is La Weina (Ravigneaux) planetary gears, coaxially arranged with input shaft 1,2, at transition axis 4 the other ends, small sun gear 62a and transition axis 4 are rigidly connected, large sun gear 62b rotates and controlled by the first break B1, the planet carrier of short planet wheel 66a and long planet wheel 66b is rigidly connected and becomes planet carrier 69, and planet carrier 69 rotates and controlled by planet gear mechanism clutch K1, second brake B2.
By controlling, break 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 synchronizer SC1, SC2 control, obtain multiple gear forward speed ratios and the speed ratio that falls back.
The second planetary gears 7 adopts single planetary gear mechanism, gear ring is fixed, sun gear 72 is rigidly connected with machine shaft 8, planet carrier 79 is rigidly connected with motor soldered tooth 71, between the planet carrier 79 of the second planetary gears 7 and jack shaft 3, motor synchronizer SC3 is set, engage motor synchronizer SC3 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 mixed power output.
Power transmission line explanation:
1 grade of power transmission line: the first synchronizer SC1 and the first fast driven gear 31 combinations, the first break 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 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 62a, short planet wheel 66a, long planet wheel 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 synchronizer SC2 and the 3rd fast driving gear 23 combinations, the first break B1 closure, second clutch C2 closure, Engine torque passes to interior input shaft 2 by clutch C2, via the second synchronizer SC2, the 3rd fast driving and driven gear 23,33, 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 62a, short planet wheel 66a, long planet wheel 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 synchronizer 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 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, now small sun gear 62a and planet carrier 69 are rigidly connected, whole planetary gears 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 synchronizer 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 synchronizer SC2, the 3rd speed is main, driven gear 23, 33, 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 62a and planet carrier 69 are rigidly connected, whole planetary gears 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 synchronizer SC1 and the second fast driven gear 32 combinations, the first break 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 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 62a, short planet wheel 66a, long planet wheel 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 synchronizer 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 clutch C2, through the second synchronizer SC2, transition axis 4, now small sun gear 62a and planet carrier 69 are rigidly connected, whole planetary gears 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 synchronizer 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 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, now small sun gear 62a and planet carrier 69 are rigidly connected, whole planetary gears 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 synchronizer 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 synchronizer SC2, transition axis 4, then through small sun gear 62a, short planet wheel 66a, long planet wheel 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 motor synchronizer SC3, pass to jack shaft 3 by EM motor power outputting power by single planetary gear mechanism 7, motor synchronizer SC3, 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 planetary gears 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 7, motor synchronizer SC3, 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 planetary gears 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 7, 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 5 by planetary gears 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 driving force of Vehicle Driving Cycle, motor EM stops power output, as generator, is driven generating.
Visible, the utility model is directly passed to jack shaft 3 by the moment of torsion of motor EM through the second planetary gears 7, pass to output shaft 5 through transition axis 4, the first planetary gears 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 planetary gears 6 causes due to gear ratio.The utility model becomes velocity attitude by the first planetary gears 6, has saved reverse gear shaft and reverse idler gear, makes structure further compact.
And the second planetary gears 7 in the utility model adopts the Placement that increases moment of torsion, guarantees car load power output performance.
Clutch, synchronizer, break course of action when table 1 has shown to realize each gear.
Table 1
Gearshift procedure illustrates:
One grade is changed second gear process: dual-clutch transmission is in one grade, and the first synchronizer SC1 and the first fast driven gear 31 be in conjunction with, the first break 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 synchronizer SC2 and the 3rd fast driving gear 23 combinations, the first break 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 synchronizer 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 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 62a, short planet wheel 66a, long planet wheel 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 synchronizer SC1 and SC2, with two break 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 power character and Economy, part still less, compacter, be more conducive to lightweight.
The utility model adopts two break B1 and B2, and a single 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, avoids the idling work interval of motor; Can realize pure electric drive, motor EM independent drive vehicles travels; Can realize combination drive, motor EM and motor 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 driving force of Vehicle Driving Cycle, motor EM stops power output, as 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 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;
Jack 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 jack shaft, be also provided with intermediate gear on described jack shaft;
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 engaging with described intermediate gear, the other end connects the first planetary gears, and the moment of torsion of described transition gear transmission is exported by output shaft through described the first planetary gears gear ratio or after becoming velocity attitude;
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. the vertical pair clutch gearbox transmission devices of putting of mixed power according to claim 1, 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 subject to the first break control, 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 is subject to second brake control.
3. the vertical pair clutch gearbox transmission devices of putting of mixed power according to claim 1, 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 |
|---|---|---|---|
| CN201420259288.XU CN203822968U (en) | 2014-05-19 | 2014-05-19 | Hybrid longitudinal dual-clutch transmission drive device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420259288.XU CN203822968U (en) | 2014-05-19 | 2014-05-19 | Hybrid longitudinal dual-clutch transmission drive device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203822968U true CN203822968U (en) | 2014-09-10 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420259288.XU Expired - Fee Related CN203822968U (en) | 2014-05-19 | 2014-05-19 | Hybrid longitudinal dual-clutch transmission drive device |
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| Country | Link |
|---|---|
| CN (1) | CN203822968U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109578533A (en) * | 2017-09-29 | 2019-04-05 | 比亚迪股份有限公司 | The electronic assembly of three gears and its speed ratio determine method |
| CN113685499A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
-
2014
- 2014-05-19 CN CN201420259288.XU patent/CN203822968U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109578533A (en) * | 2017-09-29 | 2019-04-05 | 比亚迪股份有限公司 | The electronic assembly of three gears and its speed ratio determine method |
| CN109578533B (en) * | 2017-09-29 | 2022-03-15 | 比亚迪股份有限公司 | Three-gear electric assembly and speed ratio determination method thereof |
| CN113685499A (en) * | 2020-05-18 | 2021-11-23 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
| CN113685499B (en) * | 2020-05-18 | 2024-03-22 | 广州汽车集团股份有限公司 | Nine-gear double-clutch transmission and vehicle |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 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. |
|
| 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: 20140910 Termination date: 20190519 |