CN101149095A - Hybrid power drive device based on double clutch automatic speed-changer - Google Patents
Hybrid power drive device based on double clutch automatic speed-changer Download PDFInfo
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- CN101149095A CN101149095A CNA2007100474224A CN200710047422A CN101149095A CN 101149095 A CN101149095 A CN 101149095A CN A2007100474224 A CNA2007100474224 A CN A2007100474224A CN 200710047422 A CN200710047422 A CN 200710047422A CN 101149095 A CN101149095 A CN 101149095A
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- motor
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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
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
- F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
- F16H3/725—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines with means to change ratio in the mechanical gearing
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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- Electric Propulsion And Braking For Vehicles (AREA)
Abstract
The mixed power drive unit based on double clutch automatic speed variator has one planet gear train, one double clutch automatic speed variator, three synchronizers and one brake. The planet gear train includes a planet gear, an outer gear and a sun gear; the double clutch automatic speed variator includes four shafts, two DCT clutches, four gear meshing pairs and two synchronizers. The present invention has the advantages of power synthesis between the engine and the motor with single planet gear rank, the combination with DCT, relatively broad transmission ratio range of stepless speed change and capacity of expanding the use range of engine.
Description
Technical field
The present invention relates to a kind of Power Drive Unit, particularly a kind of hybrid drive based on double-clutch automatic gearbox.
Background technique
Hybrid vehicle is replaced the important transitional product of internal-combustion engines vehicle as pure electric automobile, with the obvious advantage on fuel-saving environmental protection not only, and its power character and distance travelled also can match in excellence or beauty with present internal-combustion engines vehicle, thereby become the focus of current each big motor corporation research and development.Hybrid power transmission system is one of key technology of hybrid vehicle.Good transmission system not only can make motor performance maximal efficiency, can also ensure and the cooperating of motor, and carries out rational power division according to control strategy, thereby improves the operational efficiency of car load.At present, double clutch (Dual Clutch Transmission is called for short DCT) is applied to the German LUK of mainly containing of hybrid vehicle system development company, AM General automotive engineering company and University Of Chongqing.The designed hybrid power transmission system of LUK company combines incorporate starter/generator with DCT, compact structure, but the power coupling is a kind of strong coupling; The designed hybrid power transmission system mode of operation of General Motors Corporation is more, but structure is not compact.University Of Chongqing combines planet toothrow wheel with double clutch, have the multiple transmission mode of multiple number of gear, when carrying out transmission of power under certain pattern, motor must be in running order always, and in the transmission process, the axle of DCT can reduce certain efficient all rotating.
Summary of the invention
Technical problem of the present invention is to provide a kind of employing simple planetary arrangement to combine with the fourth gear double-clutch automatic gearbox, has the hybrid drive based on double-clutch automatic gearbox of four similar infinite variable speed driving scopes.
In order to solve above technical problem, the invention provides a kind of hybrid drive based on double-clutch automatic gearbox, comprise a motor, a motor and a clutch end, this device is provided with planetary pinion, double-clutch automatic gearbox, synchronizer C, D, E and break; Wherein planetary pinion comprises planet wheel, external toothing, sun gear, and sun gear is connected with axle P; Double-clutch automatic gearbox comprise a Q, axle R, axle S, axle T, DCT clutch A, DCT clutch B, one grade of gear engagement to, intermediate gear engagement to, three-range transmission engagement to, fourth gear engagement to, synchronizer D and synchronizer E; To being arranged on a R and the axle T, to being arranged on a R and the axle S, synchronizer D, E are connected with a R to, fourth gear engagement in the intermediate gear engagement to, three-range transmission engagement for one grade of gear engagement.
By DCT clutch A, B, synchronizer C and clutch are realized the switching of engine-driving or motor driving or motor and motor combination drive pattern.
By one grade of gear engagement to the engagement of, intermediate gear to, three-range transmission engagement to, fourth gear engagement to realizing the switching of four gears of engine-driving with synchronizer D, E, the perhaps switching of four gears of motor driving, the perhaps switching of motor and four gears of motor combination drive.
In motor drive mode, realize the regenerative braking pattern, promptly output terminal is an input end, and input end is an output terminal, and different vehicle wheel rotational speeds is realized the regenerative braking of four gears, and motor is in generating state.
Superior effect of the present invention is:
1) proposed a kind of new hybrid power transmission system, this system has power output all the time when gear shift, has improved the Economy and the travelling comfort of car load;
2) utilize single planetary row gear mesh motor and motor to carry out power and synthesize, make this transmission system have the stepless speed change function of being similar to, and combine, realize having stepless change, enlarge the using scope of motor than the big speed ratio scope with DCT;
3) can provide multiple velocity ratio during regenerative braking, thereby improve the efficient of regenerative braking.
Description of drawings
Fig. 1 is a structural representation of the present invention;
Fig. 2 is the structural representation of cold start-up of the present invention;
Fig. 3 is the structural representation of thermal starting of the present invention;
Fig. 4 is the structural representation of one grade of driving of motor of the present invention;
Fig. 5 is the structural representation that motor second gear of the present invention drives;
Fig. 6 is the structural representation that motor third gear of the present invention drives;
Fig. 7 is the structural representation that motor fourth gear of the present invention drives;
Fig. 8 is the structural representation that engine-driving of the present invention drives electric power generation;
Fig. 9 is the structural representation of one grade of combination drive of the present invention;
Figure 10 is the structural representation of combination drive second gear of the present invention;
Figure 11 is the structural representation of combination drive third gear of the present invention;
Figure 12 is the structural representation of combination drive fourth gear of the present invention;
Figure 13 is the structural representation of one grade of driving of motor of the present invention;
Figure 14 is the structural representation that motor second gear of the present invention drives;
Figure 15 is the structural representation that motor third gear of the present invention drives;
Figure 16 is the structural representation that motor fourth gear of the present invention drives;
Figure 17 is the structural representation of the regenerative braking pattern of motor third gear driving of the present invention;
The number in the figure explanation
The 1-motor; The 2-clutch;
3-axle P; 4-gear mesh M;
The 5-planet carrier; The 6-planet wheel;
The 7-external toothing; 8-axle U;
The 9-break; 10-synchronizer C;
11-gear mesh N; 12-axle V;
The 13-motor; The 14-sun gear;
15-axle Q; The 16-output terminal;
17-axle R; The engagement of 18-fourth gear is right;
19-synchronizer D; The engagement of 20-intermediate gear is right;
The engagement of 21-three-range transmission is right; 22-synchronizer E;
One grade of gear engagement of 23-is right; 24-axle S;
25-DCT clutch A; 26-axle T;
27-DCT clutch B; 28-gear W.
Embodiment
See also shown in the accompanying drawing, the invention will be further described.
As shown in Figure 1, the invention provides a kind of hybrid drive based on double-clutch automatic gearbox, comprise a motor 1, a motor 13 and a clutch end 16, this device is provided with planetary pinion, double-clutch automatic gearbox, synchronizer C10, D19, E22, break 9, axle U8, axle V12 and gear W28; Wherein planetary pinion comprises planet carrier 5, planet wheel 6, external toothing 7, sun gear 14, and sun gear 14 is connected with axle P3; Double-clutch automatic gearbox comprise a Q15, axle R17, axle S24, axle T26, DCT clutch A25, DCT clutch B27, one grade of gear engagement to 23, the intermediate gear engagement to 20, the three-range transmission engagement to 21, the fourth gear engagement to 18, synchronizer D19 and synchronizer E22; One grade of gear engagement to 23, the three-range transmission engagement is arranged on a R17 and the axle T26 21, the intermediate gear engagement to 20, the fourth gear engagement is arranged on a R17 and the axle S24 18, synchronizer D19, E22 are connected with a R17.By DCT clutch A25, B27, synchronizer C10 and clutch realize that motor 1 drives or motor 13 drives or the switching of motor 1 and motor 13 combination drive patterns.By one grade of gear engagement to 23, the intermediate gear engagement to 20, the three-range transmission engagement to 21, the fourth gear engagement realizes that with synchronizer D19, E22 motor 1 drives the switching of four gears to 18, perhaps motor 13 drives the switching of four gears, the perhaps switching of motor 1 and four gears of motor 13 combination drives.
As shown in Figure 2, transmission system for cold starting, clutch 2 combinations, combination by break 9 is with external toothing 7 lockings of planet toothrow wheel, the right combination of synchronizer C10 simultaneously, motor 13 drives DCT central shaft Q15 and drives sun gear 14 rotations through planet wheel 6, thus ato unit 1, heavy line among its power circuit such as the figure.
As shown in Figure 3, be the transmission system of thermal starting, this moment, the friction of motor 1 was less, motor 13 only some transmission of torque is given motor 1 bent axle, and can increase the clutch of a certain gear correspondence gradually, and synchronizer is engaged, strengthen the driving torque that motor 1 transmits to driving wheel gradually.Be that example describes now with one grade, during thermal starting, synchronizer C10 is right to be engaged, and passes through external toothing 7 lockings of the combination of break 9 with planet toothrow wheel, power circuit starts thereby drive motor 1 through gear mesh N11, DCT central shaft Q15, gear mesh M4, planet wheel 6 and sun gear 14.At this moment, slowly combination of DCT clutch B27, the combination of a synchronizer E22 left side so progressively strengthens the driving torque of 1 pair of vehicle of motor, heavy line among its power circuit such as the figure.Other gear and one grade are similar.
When automobile running resistance power hour, only rely on the motor single driving just can satisfy the needs that travel, as shown in Figure 4, be one grade of drive pattern of motor, motor is not worked, and clutch 2 engages, break 9 is with external toothing 7 lockings of planet toothrow wheel, DCT clutch 27 engages, and one grade of gear engagement engages heavy line among its power circuit such as the figure with synchronizer 22 to 23.
As shown in Figure 5, be motor second gear drive pattern, motor is not worked, and clutch 2 engages, and break 9 is with external toothing 7 lockings of planet toothrow wheel, and DCT clutch A25 engages, and the intermediate gear engagement engages heavy line among its power circuit such as the figure with synchronizer D19 to 20.
As shown in Figure 6, be motor third gear drive pattern, motor is not worked, and clutch 2 engages, and break 9 is with external toothing 7 lockings of planet toothrow wheel, and DCT clutch B27 engages, and the three-range transmission engagement engages heavy line among its power circuit such as the figure with synchronizer E22 to 21.
As shown in Figure 7, be motor fourth gear drive pattern, motor is not worked, and clutch 2 engages, and break 9 is with external toothing 7 lockings of planet toothrow wheel, and DCT clutch A25 engages, and the fourth gear engagement engages heavy line among its power circuit such as the figure with synchronizer D19 to 18.
Heavier or when running at high speed when vehicle load, must rely on motor and motor to drive i.e. combination drive operating mode jointly.As shown in Figure 9, for mixing one grade of driving, clutch 2 combinations, synchronizer C10 left side combination, DCT clutch B27 engages, and one grade of gear engagement engages heavy line among its power circuit such as the figure with synchronizer E22 to 23.
As shown in figure 10, drive for mixing second gear, clutch 2 engages, synchronizer C10 left side combination, and DCT clutch A25 engages, and the intermediate gear engagement engages heavy line among its power circuit such as the figure with synchronizer D19 to 20.
As shown in figure 11, drive for mixing third gear, clutch 2 engages, synchronizer C10 left side combination, and DCT clutch B27 engages, and the three-range transmission engagement engages heavy line among its power circuit such as the figure with synchronizer E22 to 21.
As shown in figure 12, drive for mixing fourth gear, clutch 2 engages, synchronizer C10 left side combination, and DCT clutch A25 engages, and the fourth gear engagement engages heavy line among its power circuit such as the figure with synchronizer D19 to 18.
As shown in figure 13, be one grade of driving of motor, the right combination of synchronizer C10, DCT clutch B27 engages, and one grade of gear engagement engages heavy line among its power circuit such as the figure with synchronizer E22 to 23.
As shown in figure 14, for the motor second gear drives, the right combination of synchronizer C10, DCT clutch A25 engages, and one grade of gear engagement engages heavy line among its power circuit such as the figure with synchronizer D19 to 20.
As shown in figure 15, for the motor third gear drives, the right combination of synchronizer C10, DCT clutch B27 engages, and the three-range transmission engagement engages heavy line among its power circuit such as the figure with synchronizer E22 to 21.
As shown in figure 16, for the motor fourth gear drives, the right combination of synchronizer C10, DCT clutch A25 engages, and the fourth gear engagement engages heavy line among its power circuit such as the figure with synchronizer D19 to 18.
In motor 13 drive patterns, realize the regenerative braking pattern, promptly output terminal is an input end, and input end is an output terminal, and different vehicle wheel rotational speeds is realized the regenerative braking of four gears, and motor 13 is in generating state.As shown in figure 17, be motor third gear drive pattern, the regenerative braking operating mode is identical with motor 13 single driving power circuit bang paths, and power flow direction is opposite, and this moment, motor 13 was in generating state, heavy line among its power circuit such as the figure.
Claims (4)
1. the hybrid drive based on double-clutch automatic gearbox comprises a motor, a motor and a clutch end, it is characterized in that:
This device is provided with planetary pinion, double-clutch automatic gearbox, synchronizer C, D, E and break; Wherein planetary pinion comprises planet wheel, external toothing, sun gear, and sun gear is connected with axle P; Double-clutch automatic gearbox comprise a Q, axle R, axle S, axle T, DCT clutch A, DCT clutch B, one grade of gear engagement to, intermediate gear engagement to, three-range transmission engagement to, fourth gear engagement to, synchronizer D and synchronizer E; To being arranged on a R and the axle T, to being arranged on a R and the axle S, synchronizer D, E are connected with a R to, fourth gear engagement in the intermediate gear engagement to, three-range transmission engagement for one grade of gear engagement.
2. by the described a kind of hybrid drive of claim 1, it is characterized in that based on double-clutch automatic gearbox:
By DCT clutch A, B, synchronizer C and clutch are realized the switching of engine-driving or motor driving or motor and motor combination drive pattern.
3. by the described a kind of hybrid drive of claim 1, it is characterized in that based on double-clutch automatic gearbox:
By one grade of gear engagement to the engagement of, intermediate gear to, three-range transmission engagement to, fourth gear engagement to realizing the switching of four gears of engine-driving with synchronizer D, E, the perhaps switching of four gears of motor driving, the perhaps switching of motor and four gears of motor combination drive.
4. by the described a kind of hybrid drive of claim 3, it is characterized in that based on double-clutch automatic gearbox:
In motor drive mode, realize the regenerative braking pattern, promptly output terminal is an input end, and input end is an output terminal, and different vehicle wheel rotational speeds is realized the regenerative braking of four gears, and motor is in generating state.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007100474224A CN101149095B (en) | 2007-10-25 | 2007-10-25 | Hybrid power drive device based on double clutch automatic speed-changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007100474224A CN101149095B (en) | 2007-10-25 | 2007-10-25 | Hybrid power drive device based on double clutch automatic speed-changer |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101149095A true CN101149095A (en) | 2008-03-26 |
| CN101149095B CN101149095B (en) | 2010-12-01 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007100474224A Active CN101149095B (en) | 2007-10-25 | 2007-10-25 | Hybrid power drive device based on double clutch automatic speed-changer |
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| CN (1) | CN101149095B (en) |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101608684A (en) * | 2009-07-15 | 2009-12-23 | 韦海虎 | A kind of mechanical continuously-variable transmission of two mixed power differential speed regulations |
| CN101900190A (en) * | 2010-09-16 | 2010-12-01 | 重庆嘉卡变速箱有限公司 | Auto continuously variable transmission |
| CN102211577A (en) * | 2010-04-02 | 2011-10-12 | 通用汽车环球科技运作有限责任公司 | Method and apparatus for clutch control in a vehicle having an engine start-stop powertrain and a dual-clutch transmission |
| WO2012000143A1 (en) * | 2010-06-30 | 2012-01-05 | 上海捷能汽车技术有限公司 | Vehicle shift control method and device of dual-clutch power coupling synchronizer |
| WO2012000142A1 (en) * | 2010-06-30 | 2012-01-05 | 上海捷能汽车技术有限公司 | Vehicle shift control method and device of dual-clutch power coupling synchronizer |
| CN102717714A (en) * | 2012-06-08 | 2012-10-10 | 北京汽车新能源汽车有限公司 | Pure electric vehicle braking energy recovery control system and method based on DCT (Data Communication Terminal) |
| CN102770300A (en) * | 2010-02-19 | 2012-11-07 | 莲花汽车有限公司 | A land vehicle driven by an electric or hydraulic motor |
| CN103256353A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Double-planet-row converging type multi-clutch speed variator |
| CN103277466A (en) * | 2013-04-28 | 2013-09-04 | 河南科技大学 | Multi-clutch speed changer |
| CN104081087A (en) * | 2012-02-06 | 2014-10-01 | 腓特烈斯港齿轮工厂股份公司 | Multi-ratio transmission |
| CN104819262A (en) * | 2015-05-21 | 2015-08-05 | 山东科技大学 | Automobile dual-clutch transmission gear shifting mechanism |
| CN105715785A (en) * | 2014-12-19 | 2016-06-29 | 保时捷股份公司 | Power drive unit for motor vehicle |
| CN106585362A (en) * | 2015-10-13 | 2017-04-26 | 广州汽车集团股份有限公司 | Dynamic coupling system of hybrid electric vehicle and control method of dynamic coupling system |
| CN109383265A (en) * | 2017-12-13 | 2019-02-26 | 宁波圣龙汽车动力***股份有限公司 | A kind of hybrid power gearbox structure and its working method |
| WO2019080470A1 (en) * | 2017-10-25 | 2019-05-02 | 盐城市步高汽配制造有限公司 | Two-gear intermediate shaft transmission structure |
| CN113775712A (en) * | 2021-09-23 | 2021-12-10 | 华南理工大学 | Mechanical transmission and control |
-
2007
- 2007-10-25 CN CN2007100474224A patent/CN101149095B/en active Active
Cited By (26)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101608684A (en) * | 2009-07-15 | 2009-12-23 | 韦海虎 | A kind of mechanical continuously-variable transmission of two mixed power differential speed regulations |
| CN102770300A (en) * | 2010-02-19 | 2012-11-07 | 莲花汽车有限公司 | A land vehicle driven by an electric or hydraulic motor |
| CN102211577A (en) * | 2010-04-02 | 2011-10-12 | 通用汽车环球科技运作有限责任公司 | Method and apparatus for clutch control in a vehicle having an engine start-stop powertrain and a dual-clutch transmission |
| CN102211577B (en) * | 2010-04-02 | 2014-10-22 | 通用汽车环球科技运作有限责任公司 | Method and apparatus for clutch control in a vehicle having an engine start-stop powertrain and a dual-clutch transmission |
| CN102310852B (en) * | 2010-06-30 | 2014-12-17 | 上海捷能汽车技术有限公司 | Gear shifting control method for automobile double-clutch power coupling synchronizer and device thereof |
| WO2012000143A1 (en) * | 2010-06-30 | 2012-01-05 | 上海捷能汽车技术有限公司 | Vehicle shift control method and device of dual-clutch power coupling synchronizer |
| WO2012000142A1 (en) * | 2010-06-30 | 2012-01-05 | 上海捷能汽车技术有限公司 | Vehicle shift control method and device of dual-clutch power coupling synchronizer |
| CN102310852A (en) * | 2010-06-30 | 2012-01-11 | 上海捷能汽车技术有限公司 | Gear shifting control method for automobile double-clutch power coupling synchronizer and device thereof |
| CN101900190B (en) * | 2010-09-16 | 2012-05-23 | 重庆嘉卡变速箱有限公司 | Auto continuously variable transmission |
| CN101900190A (en) * | 2010-09-16 | 2010-12-01 | 重庆嘉卡变速箱有限公司 | Auto continuously variable transmission |
| CN104081087A (en) * | 2012-02-06 | 2014-10-01 | 腓特烈斯港齿轮工厂股份公司 | Multi-ratio transmission |
| CN104081087B (en) * | 2012-02-06 | 2016-11-09 | 腓特烈斯港齿轮工厂股份公司 | Multiple-speed gear-box |
| CN102717714A (en) * | 2012-06-08 | 2012-10-10 | 北京汽车新能源汽车有限公司 | Pure electric vehicle braking energy recovery control system and method based on DCT (Data Communication Terminal) |
| CN103256353A (en) * | 2013-04-28 | 2013-08-21 | 河南科技大学 | Double-planet-row converging type multi-clutch speed variator |
| CN103277466A (en) * | 2013-04-28 | 2013-09-04 | 河南科技大学 | Multi-clutch speed changer |
| CN103277466B (en) * | 2013-04-28 | 2015-07-15 | 河南科技大学 | Multi-clutch speed changer |
| CN103256353B (en) * | 2013-04-28 | 2015-08-12 | 河南科技大学 | Double planet wheel rows of mixing convergent current type multi-clutch speed change gear |
| CN105715785A (en) * | 2014-12-19 | 2016-06-29 | 保时捷股份公司 | Power drive unit for motor vehicle |
| CN105715785B (en) * | 2014-12-19 | 2017-11-03 | 保时捷股份公司 | Power-driven gear for motor vehicles |
| CN104819262A (en) * | 2015-05-21 | 2015-08-05 | 山东科技大学 | Automobile dual-clutch transmission gear shifting mechanism |
| CN106585362A (en) * | 2015-10-13 | 2017-04-26 | 广州汽车集团股份有限公司 | Dynamic coupling system of hybrid electric vehicle and control method of dynamic coupling system |
| WO2019080470A1 (en) * | 2017-10-25 | 2019-05-02 | 盐城市步高汽配制造有限公司 | Two-gear intermediate shaft transmission structure |
| CN109383265A (en) * | 2017-12-13 | 2019-02-26 | 宁波圣龙汽车动力***股份有限公司 | A kind of hybrid power gearbox structure and its working method |
| CN109383265B (en) * | 2017-12-13 | 2024-05-03 | 宁波圣龙汽车动力***股份有限公司 | Hybrid power gearbox structure and working method thereof |
| CN113775712A (en) * | 2021-09-23 | 2021-12-10 | 华南理工大学 | Mechanical transmission and control |
| CN113775712B (en) * | 2021-09-23 | 2023-07-18 | 华南理工大学 | Mechanical transmission and control |
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|---|---|
| CN101149095B (en) | 2010-12-01 |
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