CN204895105U - 2AT derailleur and hybrid system for hybrid vehicle - Google Patents
2AT derailleur and hybrid system for hybrid vehicle Download PDFInfo
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- CN204895105U CN204895105U CN201520656598.XU CN201520656598U CN204895105U CN 204895105 U CN204895105 U CN 204895105U CN 201520656598 U CN201520656598 U CN 201520656598U CN 204895105 U CN204895105 U CN 204895105U
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Abstract
The utility model relates to a 2AT derailleur and hybrid system for hybrid vehicle is including clutch C1, clutch C2, clutch C3, stopper B1, planet row assembly P1, P1 input shaft, P1 output shaft, P1 owner driving gear, differential mechanism, main slow down driven gear, planet row assembly P2, P2 input shaft, P2 output shaft and the P2 owner driving gear that slows down that slows down. Adopting the 2AT derailleur and hybrid system for hybrid vehicle of this kind of structure, adopting the two countershaft structures of dual input axle, simple structure is compact, and control is convenient, has adopted 3 double clutch, stopper and the 2 planet rows of group, and a set of gear pair and a differential mechanism structure through a set of clutch engine and derailleur, make both power transmit or to break off, in unpowered interrupt basically in service, it is smooth -going to shift, and effectual reduction battery cost improves acceleration performance to charge to the battery through the engine, make and charge more in a flexible way, improve the continuous mileage of sailing.
Description
Technical field
The utility model relates to vehicle drive system technical field, particularly relates to the gear arrangement field being applied to hybrid power, specifically refers to a kind of the 2AT change-speed box and the hybrid power system that are applied to motor vehicle driven by mixed power.
Background technology
Electronlmobil is as a kind of walking-replacing tool, it has environmentally friendly, to advantages such as oil interdependency are low, but it is high to there is battery cost in current pure electric automobile, the shortcomings such as continual mileage is low, and charging is inconvenient, current battery-driven car generally adopts and singly keeps off slowing-down structure, cause the efficient district relative narrower of motor, cause economy poor.Therefore be badly in need of a kind of environmentally friendly, and continual mileage is high, the automobile transmission of economy and good dynamic property.
Utility model content
The purpose of this utility model is the shortcoming overcoming above-mentioned prior art, the 2AT change-speed box being applied to motor vehicle driven by mixed power provide and a kind ofly can realize effectively reducing battery cost, improve acceleration capability, charging is more flexible, simple and compact for structure, having broader applications scope and hybrid power system.
To achieve these goals, of the present utility model be applied to motor vehicle driven by mixed power 2AT change-speed box and hybrid power system there is following formation:
This is applied to the 2AT change-speed box of motor vehicle driven by mixed power, and its principal feature is, described change-speed box comprises power-transfer clutch C1, power-transfer clutch C2, power-transfer clutch C3, drg B1, planet row assembly P1, P1 input shaft, P1 output shaft, the main deceleration driving gear of P1, diff, main reduction driven gear, planet row assembly P2, P2 input shaft, P2 output shaft and the main deceleration driving gear of P2, described P1 input shaft is connected between described power-transfer clutch C1 and planet row assembly P1, described P1 output shaft is connected with described planet row assembly P1, described P1 main deceleration driving gear rigidity is arranged on described P1 output shaft, described main reduction driven gear rigidity is arranged on described diff, described P2 input shaft is connected between described power-transfer clutch C2 and planet row assembly P2, described power-transfer clutch C3 is connected between described P2 input shaft and planet row assembly P2, described drg B1 and described planet row assembly P2 is rigidly connected, and described P2 main deceleration driving gear rigidity is arranged on described P2 output shaft.
Preferably, described planet row assembly P1 comprises sun wheel P11, satellite gear P12, gear ring P13 and pinion carrier P14, described P1 input shaft and described sun wheel P11 are rigidly connected, described gear ring P13 and case of transmission are rigidly connected, and described pinion carrier P14 and described P1 output shaft are rigidly connected.
Preferably, described planet row assembly P2 comprises sun wheel P21, satellite gear P22, gear ring P23 and pinion carrier P24, described power-transfer clutch C3 is connected with described gear ring P23, described drg B1 is arranged on case of transmission, described P2 input shaft and sun wheel P21 are rigidly connected, described gear ring P23 and drg B1 one end are rigidly connected, and described pinion carrier P24 and P2 output shaft are rigidly connected.
The utility model also relates to a kind of hybrid power system being applied to motor vehicle driven by mixed power comprising described change-speed box, it is characterized in that, described system also comprises motor, motor output shaft, driving engine and engine output shaft, described motor is connected with described power-transfer clutch C1 by described motor output shaft, and described driving engine is connected with described power-transfer clutch C2 by described engine output shaft.
Preferably, when being in pure mechanical one grade of drive pattern, described power-transfer clutch C1 disconnects, described power-transfer clutch C2 and power-transfer clutch C3 closes, described drg B1 disconnects, and when being in pure mechanical second gear drive pattern, described power-transfer clutch C1 and power-transfer clutch C3 disconnects, described power-transfer clutch C2 closes, and described drg B1 closes.
Preferably, when being in pure motorized motions pattern, described power-transfer clutch C1 closes, and described power-transfer clutch C2 disconnects.
Preferably, when being in one grade of combination drive pattern, described power-transfer clutch C1, power-transfer clutch C2 and power-transfer clutch C3 are all closed, described drg B1 disconnects, when being in second gear combination drive pattern, described power-transfer clutch C1 and power-transfer clutch C2 closes, and described power-transfer clutch C3 disconnects, and described drg B1 closes.
Preferably, when being in one grade of engine drive and power generation mode, described power-transfer clutch C1, power-transfer clutch C2 and power-transfer clutch C3 are all closed, described drg B1 disconnects, when being in second gear engine drive and power generation mode, described power-transfer clutch C1 and power-transfer clutch C2 closes, and described power-transfer clutch C3 disconnects, and described drg B1 closes.
Preferably, when be in pure electricity reverse gear drive pattern time, described power-transfer clutch C1 closes, and described power-transfer clutch C2 disconnects.
Have employed the 2AT change-speed box being applied to motor vehicle driven by mixed power in this utility model and hybrid power system, there is following beneficial effect:
This patent adopts dual input shaft two-pack axle construction, simple and compact for structure, and it is convenient to control, have employed 3 double-clutchs, a drg and 2 groups of planet rows, one group of gear pair and a differential design, by one group of power-transfer clutch connecting engine and change-speed box, both power are enable to transmit or disconnect; Connect motor and change-speed box by one group of power-transfer clutch, enable both power transmit or disconnect; Adopt one group of single-stage planetary row mechanism to realize motor input to slow down; Adopt one group of single-stage planetary row mechanism to coordinate one group of power-transfer clutch and one group of drg to realize driving engine and input 2 kinds of speed ratios outputs.This patent realizes pure Mechanical Driven by control 3 groups of power-transfer clutch break-makes and one group of drg break-make, pure motor drives, the multiple-working mode such as combination drive and generating, be in operation essentially no power interruption, and smooth gear shifting effectively reduces battery cost, improve acceleration capability, and charged to battery by driving engine, make charging more flexible, improve continual mileage.
Accompanying drawing explanation
Fig. 1 is the structural representation being applied to the hybrid power system of motor vehicle driven by mixed power of the present utility model.
Fig. 2 is the structural representation of planet row assembly P1 of the present utility model.
Fig. 3 is the structural representation of planet row assembly P2 of the present utility model.
Fig. 4 is the lateral plan being applied to the 2AT change-speed box of motor vehicle driven by mixed power of the present utility model.
Detailed description of the invention
In order to more clearly describe technology contents of the present utility model, conduct further description below in conjunction with specific embodiment.
As shown in figures 1-4, described motor vehicle driven by mixed power change-speed box has power-transfer clutch C1, power-transfer clutch C2, power-transfer clutch C3, drg B1, planet row assembly P1, the main deceleration driving gear 31 of P1 input shaft 2, P1 output shaft 3, P1, diff 4, main reduction driven gear 41, planet row assembly P2, P2 input shaft 6, the main deceleration driving gear 71 of P2 output shaft 7, P2.Described planet row assembly P1 has sun wheel P11, satellite gear P12, gear ring P13, pinion carrier P14; Described planet row assembly P2 has sun wheel P21, satellite gear P22, gear ring P23, pinion carrier P24.
Described power-transfer clutch C1 one end is rigidly connected motor output shaft, and one end is rigidly connected P1 input shaft 2; Described P1 input shaft 2 is rigidly connected with sun wheel P11, and described gear ring P13 and case of transmission are rigidly connected, and described pinion carrier P14 and P1 output shaft 3 are rigidly connected, and the main deceleration driving gear 31 of described P1 is arranged rigidly on P1 output shaft 3; Described main reduction driven gear 41 is arranged rigidly on diff 4, and described main deceleration driving gear 31 and main reduction driven gear 41 partner gear pair.
Described power-transfer clutch C2 one end is rigidly connected engine output shaft, and one end is rigidly connected P2 input shaft 6; Described power-transfer clutch C3 one end connects P2 input shaft 5, one end connects gear ring P23, described drg B1 is arranged on case of transmission, described P2 input shaft 6 is rigidly connected with sun wheel P21, described gear ring P23 and drg B1 one end are rigidly connected, described pinion carrier P24 and P2 output shaft 7 are rigidly connected, and the main deceleration driving gear 71 of described P2 is arranged rigidly on P2 output shaft 7; Described main deceleration driving gear 71 and main reduction driven gear 41 partner gear pair.
When power-transfer clutch C1 disconnects, power-transfer clutch C2 closes, power-transfer clutch C3 closes, drg B1 disconnects, and motor power cuts off, and engine power inputs, P2 input shaft 6 rigidity is connected by power-transfer clutch C3, rotating speed is identical, and namely planet row assembly P2 input and output rotating speed is identical, and motor vehicle driven by mixed power is in a pure mechanical gear drive pattern;
When power-transfer clutch C1 disconnects, power-transfer clutch C2 closes, power-transfer clutch C3 disconnects, drg B1 closes, motor power cuts off, and engine power inputs, and gear ring P23 is rigidly connected by drg B1 and case of transmission, planet row assembly P2 retarder exports, and motor vehicle driven by mixed power is in pure mechanical two gear drive patterns;
When power-transfer clutch C1 closes, power-transfer clutch C2 disconnects, and motor power inputs, and engine power cuts off, motor power input, and planet row assembly P1 slows down output, and motor vehicle driven by mixed power is in pure electric drive mode;
When power-transfer clutch C1 closes, power-transfer clutch C2 closes, power-transfer clutch C3 closes, and drg B1 disconnects, and motor power inputs, engine power inputs, planet row assembly P1 slows down output, and P2 input shaft 6 rigidity is connected by power-transfer clutch C3, and rotating speed is identical, namely planet row assembly P2 input and output rotating speed is identical, and motor vehicle driven by mixed power is in a gear combination drive pattern;
When power-transfer clutch C1 closes, power-transfer clutch C2 closes, power-transfer clutch C3 disconnects, drg B1 closes, and motor power inputs, and engine power inputs, planet row assembly P1 slows down output, gear ring P23 is rigidly connected by drg B1 and case of transmission, and planet row assembly P2 retarder exports, and motor vehicle driven by mixed power is in two gear combination drive patterns;
When power-transfer clutch C1 closes, power-transfer clutch C2 closes, power-transfer clutch C3 closes, and drg B1 disconnects, electric power generation, engine power inputs, planet row assembly P1 transmits power to motor, and P2 input shaft 6 rigidity is connected by power-transfer clutch C3, and rotating speed is identical, planet row assembly P2 input and output rotating speed is identical, and motor vehicle driven by mixed power is in gear engine drive and a power generation mode;
When power-transfer clutch C1 closes, power-transfer clutch C2 closes, power-transfer clutch C3 disconnects, drg B1 closes, electric power generation, and engine power inputs, planet row assembly P1 transmits power to motor, gear ring P23 is rigidly connected by drg B1 and case of transmission, and planet row assembly P2 retarder exports, and motor vehicle driven by mixed power is in two gear engine drive and power generation modes;
When power-transfer clutch C1 closes, power-transfer clutch C2 disconnects, and motor reversal power inputs, and engine power cuts off, and motor power input, planet row assembly P1 slows down output, and motor vehicle driven by mixed power is in pure electric reverse drive pattern.
Its principle of work is as shown below:
Table 1
(note: driving engine: zero representative starts, × close; Motor: zero representative starts, × close; Power-transfer clutch: zero representative is closed, × disconnect; Drg: zero representative is closed, × disconnect)
Have employed the 2AT change-speed box being applied to motor vehicle driven by mixed power in this utility model and hybrid power system, there is following beneficial effect:
This patent adopts dual input shaft two-pack axle construction, simple and compact for structure, and it is convenient to control, have employed 3 double-clutchs, a drg and 2 groups of planet rows, one group of gear pair and a differential design, by one group of power-transfer clutch connecting engine and change-speed box, both power are enable to transmit or disconnect; Connect motor and change-speed box by one group of power-transfer clutch, enable both power transmit or disconnect; Adopt one group of single-stage planetary row mechanism to realize motor input to slow down; Adopt one group of single-stage planetary row mechanism to coordinate one group of power-transfer clutch and one group of drg to realize driving engine and input 2 kinds of speed ratios outputs.This patent realizes pure Mechanical Driven by control 3 groups of power-transfer clutch break-makes and one group of drg break-make, pure motor drives, the multiple-working mode such as combination drive and generating, be in operation essentially no power interruption, and smooth gear shifting effectively reduces battery cost, improve acceleration capability, and charged to battery by driving engine, make charging more flexible, improve continual mileage.
In this description, the utility model is described with reference to its specific embodiment.But, still can make various amendment and conversion obviously and not deviate from spirit and scope of the present utility model.Therefore, specification sheets and accompanying drawing are regarded in an illustrative, rather than a restrictive.
Claims (9)
1. be applied to a 2AT change-speed box for motor vehicle driven by mixed power, it is characterized in that, described change-speed box comprises power-transfer clutch C1, power-transfer clutch C2, power-transfer clutch C3, drg B1, planet row assembly P1, P1 input shaft, P1 output shaft, the main deceleration driving gear of P1, diff, main reduction driven gear, planet row assembly P2, P2 input shaft, P2 output shaft and the main deceleration driving gear of P2, described P1 input shaft is connected between described power-transfer clutch C1 and planet row assembly P1, described P1 output shaft is connected with described planet row assembly P1, described P1 main deceleration driving gear rigidity is arranged on described P1 output shaft, described main reduction driven gear rigidity is arranged on described diff, described P2 input shaft is connected between described power-transfer clutch C2 and planet row assembly P2, described power-transfer clutch C3 is connected between described P2 input shaft and planet row assembly P2, described drg B1 and described planet row assembly P2 is rigidly connected, and described P2 main deceleration driving gear rigidity is arranged on described P2 output shaft.
2. the 2AT change-speed box being applied to motor vehicle driven by mixed power according to claim 1, it is characterized in that, described planet row assembly P1 comprises sun wheel P11, satellite gear P12, gear ring P13 and pinion carrier P14, described P1 input shaft and described sun wheel P11 are rigidly connected, described gear ring P13 and case of transmission are rigidly connected, and described pinion carrier P14 and described P1 output shaft are rigidly connected.
3. the 2AT change-speed box being applied to motor vehicle driven by mixed power according to claim 1, it is characterized in that, described planet row assembly P2 comprises sun wheel P21, satellite gear P22, gear ring P23 and pinion carrier P24, described power-transfer clutch C3 is connected with described gear ring P23, described drg B1 is arranged on case of transmission, described P2 input shaft and sun wheel P21 are rigidly connected, and described gear ring P23 and drg B1 one end are rigidly connected, and described pinion carrier P24 and P2 output shaft are rigidly connected.
4. one kind comprises the hybrid power system being applied to motor vehicle driven by mixed power of the change-speed box according to any one of claims 1 to 3, it is characterized in that, described system also comprises motor, motor output shaft, driving engine and engine output shaft, described motor is connected with described power-transfer clutch C1 by described motor output shaft, and described driving engine is connected with described power-transfer clutch C2 by described engine output shaft.
5. the hybrid power system being applied to motor vehicle driven by mixed power according to claim 4, it is characterized in that, when being in pure mechanical one grade of drive pattern, described power-transfer clutch C1 disconnects, and described power-transfer clutch C2 and power-transfer clutch C3 closes, and described drg B1 disconnects, when being in pure mechanical second gear drive pattern, described power-transfer clutch C1 and power-transfer clutch C3 disconnects, and described power-transfer clutch C2 closes, and described drg B1 closes.
6. the hybrid power system being applied to motor vehicle driven by mixed power according to claim 4, is characterized in that, when being in pure motorized motions pattern, described power-transfer clutch C1 closes, and described power-transfer clutch C2 disconnects.
7. the hybrid power system being applied to motor vehicle driven by mixed power according to claim 4, it is characterized in that, when being in one grade of combination drive pattern, described power-transfer clutch C1, power-transfer clutch C2 and power-transfer clutch C3 are all closed, described drg B1 disconnects, and when being in second gear combination drive pattern, described power-transfer clutch C1 and power-transfer clutch C2 closes, described power-transfer clutch C3 disconnects, and described drg B1 closes.
8. the hybrid power system being applied to motor vehicle driven by mixed power according to claim 4, it is characterized in that, when being in one grade of engine drive and power generation mode, described power-transfer clutch C1, power-transfer clutch C2 and power-transfer clutch C3 are all closed, described drg B1 disconnects, and when being in second gear engine drive and power generation mode, described power-transfer clutch C1 and power-transfer clutch C2 closes, described power-transfer clutch C3 disconnects, and described drg B1 closes.
9. the hybrid power system being applied to motor vehicle driven by mixed power according to claim 4, is characterized in that, when be in pure electricity reverse gear drive pattern time, described power-transfer clutch C1 closes, and described power-transfer clutch C2 disconnects.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520656598.XU CN204895105U (en) | 2015-08-27 | 2015-08-27 | 2AT derailleur and hybrid system for hybrid vehicle |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520656598.XU CN204895105U (en) | 2015-08-27 | 2015-08-27 | 2AT derailleur and hybrid system for hybrid vehicle |
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| CN204895105U true CN204895105U (en) | 2015-12-23 |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105882380A (en) * | 2016-04-08 | 2016-08-24 | 上海中科深江电动车辆有限公司 | Hybrid power device |
| CN105972165A (en) * | 2016-07-29 | 2016-09-28 | 重庆青山工业有限责任公司 | Double-clutch planet row type blade electric vehicle transmission |
| CN106382349A (en) * | 2016-12-07 | 2017-02-08 | 天津天海同步集团有限公司 | Double-motor compact transmission without power failure |
| CN107989980A (en) * | 2018-01-10 | 2018-05-04 | 西安卓士博液压工程有限责任公司 | A kind of hybrid drive and method |
| CN108001202A (en) * | 2016-10-31 | 2018-05-08 | 比亚迪股份有限公司 | The power drive system of vehicle and there is its vehicle |
| CN109130830A (en) * | 2018-09-04 | 2019-01-04 | 宁波上中下自动变速器有限公司 | Speed changer and dynamical system for hybrid vehicle |
| CN111284321A (en) * | 2018-12-08 | 2020-06-16 | 博格华纳公司 | Drive train for a hybrid vehicle |
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2015
- 2015-08-27 CN CN201520656598.XU patent/CN204895105U/en active Active
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105882380A (en) * | 2016-04-08 | 2016-08-24 | 上海中科深江电动车辆有限公司 | Hybrid power device |
| CN105882380B (en) * | 2016-04-08 | 2018-07-03 | 上海中科深江电动车辆有限公司 | Mixed power plant |
| CN105972165A (en) * | 2016-07-29 | 2016-09-28 | 重庆青山工业有限责任公司 | Double-clutch planet row type blade electric vehicle transmission |
| CN108001202A (en) * | 2016-10-31 | 2018-05-08 | 比亚迪股份有限公司 | The power drive system of vehicle and there is its vehicle |
| CN108001202B (en) * | 2016-10-31 | 2020-02-21 | 比亚迪股份有限公司 | Power transmission system of vehicle and vehicle with same |
| CN106382349A (en) * | 2016-12-07 | 2017-02-08 | 天津天海同步集团有限公司 | Double-motor compact transmission without power failure |
| CN107989980A (en) * | 2018-01-10 | 2018-05-04 | 西安卓士博液压工程有限责任公司 | A kind of hybrid drive and method |
| CN107989980B (en) * | 2018-01-10 | 2023-09-05 | 西安卓士博液压工程有限责任公司 | Hybrid power driving device and method |
| CN109130830A (en) * | 2018-09-04 | 2019-01-04 | 宁波上中下自动变速器有限公司 | Speed changer and dynamical system for hybrid vehicle |
| CN109130830B (en) * | 2018-09-04 | 2024-02-23 | 宁波上中下自动变速器有限公司 | Transmission and power system for hybrid vehicle |
| CN111284321A (en) * | 2018-12-08 | 2020-06-16 | 博格华纳公司 | Drive train for a hybrid vehicle |
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