CN102616127B - Hybrid power transmission device of dual-mode two-stage planet wheel - Google Patents
Hybrid power transmission device of dual-mode two-stage planet wheel Download PDFInfo
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- CN102616127B CN102616127B CN201210097446.1A CN201210097446A CN102616127B CN 102616127 B CN102616127 B CN 102616127B CN 201210097446 A CN201210097446 A CN 201210097446A CN 102616127 B CN102616127 B CN 102616127B
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Abstract
The invention discloses a hybrid power transmission device of a dual-mode two-stage planet wheel. The hybrid power transmission device comprises an engine, a first motor, a second motor, a planet carrier and a differential, wherein a first planet row and a second planet row are arranged on the planet carrier, the first planet row comprises a first-stage planet wheel and a second-stage planet wheel, the second planet row also comprises the first-stage planet wheel and the second-stage planet wheel, an outer gear ring of the first planet row is connected with the engine, the second motor is connected with a sun wheel of the first planet row, and the outer gear ring of the second planet row is connected with the differential; and the first motor is connected with the planet carrier, and the planet carrier is connected with the outer gear ring of the first planet row by closing a second wet type clutch. The hybrid power transmission device of the dual-mode two-stage planet wheel can realize a variety of working modes, reduce the requirements on the rotational speed and the torque of the motors and reduce the technical requirements on the motors, and the direct effect is that the difficulty in processing and manufacturing of the motors is reduced.
Description
Technical field
The present invention relates to a kind of hybrid transmissions, especially a kind of driving device that adopts Planetary Gear Transmission.
Technical background
Hybrid vehicle is as a kind of emerging energy-efficient, environment-friendly automobiles, its technology and market are in a kind of vigorous growth stage, pay attention to and help the hybrid vehicle industry of China, being the development opportunity of shortening fast and world car technical merit gap, is also the important opportunity that ensures China's auto trade healthy and sustainable development.Hybrid vehicle (HEV) is compared with orthodox car and pure electric automobile, and maximum differential is power system.For in parallel and series parallel type HEV, dynamic coupling system is responsible for a plurality of power pack of HEV to be combined, realize between multi power source reasonably power division and power is passed to drive axle, it in HEV exploitation in critical role, its performance is directly connected to HEV vehicle performance and whether reaches designing requirement, is the most crucial part of HEV.Planet circular system has multiple degree of freedom, input and output controlled feature flexibly, therefore, and compact conformation, volume is little, speed ratio is large, adopted by increasing hybrid electric vehicle power coupled system, this is also a kind of trend of current hybrid power automobile power assembly development.
Within 1997, Toyota releases first hybrid vehicle Prius, within 2005, released again carry up-to-date the 3rd generation electromechanical mixing dynamic force system 2006 sections of Prius, still adopt THS series parallel type structure, dexterous accurate planetary gear system is redistributed the horsepower output of driving engine, reaches the object of reasonable balanced engine load.Shown in Fig. 1, be Toyota Prius hybrid transmissions constructional drawing, wherein 1, driving engine, 2, bent axle, 3, retarder, 4, electrical generator MG1,5, planetary gear train, 6, sun wheel, 7, satellite gear, 8, external toothing, 8a, gear ring drive sprocket, 9, pinion carrier, 10, silent chain, 11, reducing gear, 12, ring gear.13, reducing gear, 14, diff, 15a, b, driving wheel, 16, electrical motor MG2.Its hybrid power system assembly is comprised of parts such as driving engine (Engine), electrical generator (MG1), electrical motor (MG2), dynamic coupling system, inverter and power accumulators.In Ci mechanism, driving engine and pinion carrier are connected, by planetary wheel by transmission of power to external toothing and sun wheel, gear ring axle and electrical motor and transmission shaft are connected, sun wheel shaft and generator electric.This system is directly delivered to the most of torque of driving engine on axle drive shaft, and fraction torque is passed to electrical generator, and the electric energy that electrical generator sends charges or electrical motor for battery according to instruction, to increase propulsive effort.This structure can change it by regulator generator rotating speed, makes driving engine always in high efficient area or Low Emission Zone.In addition,, by regulating the rotating speed of each element of planet row, it is worked as toric transmission.
This constructional feature:
1) dynamic coupling system has adopted single planetary row three shaft transmission systems;
2) two motors are arranged in the both sides of planet row;
3) between the output gear of planet row and counter gear shaft, adopted chain drive technology;
4), because planetary wheel is realized electrodeless variable-speed, engine speed and the speed of a motor vehicle do not have direct relation; And driving engine is main power, in whole service process, driving engine provides whole energy.Therefore, the key that car load is controlled is to find the best efficiency point of driving engine under certain power, by regulating the rotating speed of motor M G1 to realize engine optimization, controls.
5) motor M G2 output shaft and planet row external toothing are affixed, during pure electronic starting, only need to control MG2, and it is very simple that system drive is controlled realization.
prior art shortcoming
1, motor arrangement mode
Two motor arrangements are in the both sides of planet row, and cooling system complicated layout, electric system integrated level is low and left and right, planet row both sides transmission shaft is not isometric, are unfavorable for that front deck arranges.Motor M G1 and driving engine are arranged side by side in planet row right side, because both distances are closer, and the optimum working temperature of MG1 is 60 ℃ and is less than 90 ℃ of driving engine optimum working temperatures, therefore the impact that MG1 housing can be subject to motor body heat radiation raises fast, can cause the often mode of operation in cooling MG1 of electromotor cooling system, affect car load efficiency.Due to MG1 and the shared a set of cooling system of MG2, MG1 and MG2 are arranged in the both sides of planet row, cooling system more complicated, and integrated level is low, has brought cost increase, and reliability is low.
2, single planet circular system reduction ratio is too low impacts system
(a) hybrid power system requires too high to motor performance
The rotation speed change wide ranges of hybrid power system to motor, very harsh to motor accuracy of manufacture, rotating speed/torque characteristics and requirement for dynamic balance thereof.
(b) hybrid power system is too high to space arrangement requirement;
In order to reach enough reduction ratios, transmission gear deceleration system is too high to space arrangement requirement, and this speed reduction gearing has adopted and comprised chain-drive Multi-stage transmission parts, has further strengthened the complexity of system.
3, the latch functions of motor M G1 disappearance, under some operating mode, its work efficiency declines obviously;
In some vehicle driving-cycle process, because having caused motor M G1, demand power unsteady always need to be controlled at the power stage that zero rotating speed fluctuates to regulate driving engine.Under this operating mode, the work efficiency of MG1 is very low, and the horsepower output of system and power demand always have some fluctuations, also has certain hysteresis quality, and this has all increased the upper difficulty of controlling.
Summary of the invention
technical matters:
The present invention is exactly in order to overcome above-mentioned shortcoming, designed and developed the bimodulus two-stage satellite gear hybrid transmissions of a set of hybrid electric vehicle special use, by structure design cleverly, realize efficient transmission, the requirement of the end to the rotating speed of motor and torque can be fallen simultaneously, can realize the coupling of hybrid vehicle multi power source, realize the requirement of the various functions of hybrid vehicle control.
technical scheme:
For solving the problems of the technologies described above, the technical solution used in the present invention is: a kind of bimodulus two-stage satellite gear hybrid transmissions, comprise driving engine, the first motor, the second motor, pinion carrier and diff, it is characterized in that: in described pinion carrier, be provided with the first planet row and the second planet row, first order satellite gear and second stage satellite gear are drawn together in the first described planet package, the second described planet row also comprises first order satellite gear and second stage satellite gear, the first order satellite gear of the first described planet row and the engagement of the sun wheel of the first planet row, the second stage satellite gear of the first described planet row and the engagement of the external toothing of the first planet row, the first order satellite gear of the second described planet row and the engagement of the sun wheel of the second planet row, the second stage satellite gear of the second described planet row and the engagement of the external toothing of the second planet row, the second stage satellite gear of the second stage satellite gear of the first described planet row and the second described planet row also meshes, the external toothing of the first described planet row is connected with described driving engine, the second described motor is connected with the sun wheel of the first planet row, the sun wheel of the first described planet row is also connected with the sun wheel of the second planet row by the closure of the first liquid clutch, and the external toothing of the second described planet row is connected with described diff, the first described motor is connected with described pinion carrier, the closure of described pinion carrier by the second liquid clutch and the first planet row external toothing be connected.
In described pinion carrier, be also provided with the first drg of this pinion carrier of locking, on the second described planet row, be also provided with the second brake of a locking second planet row sun wheel.
Innovative point of the present invention:
(1) this bimodulus two-stage satellite gear hybrid transmissions is that a domestic original electromechanical integration hybrid power speed change system drives assembly, and its core is the capable five shaft gear driving systems of arranging of double star;
(2) double-motor is arranged in the homonymy of planet row, and engine position is at planet row opposite side, and it is controlled and more easy of integrationization of cooling system;
(3) double-motor is arranged in planet row homonymy, can realize the integrated of motor manufacture and fit on, reduces driving system volume, is conducive to complete vehicle structure and arranges;
(4) adopt two-stage planet gear transmission, can realize under pure electronic operating mode, motor speed direction is synchronizeed with output shaft rotary speed direction;
(5) when engine starting, according to the difference of operating mode, can use the independent start the engine of motor M G2 by controlling B1 locking pinion carrier C, or by C2 be coupled external toothing r1 and pinion carrier C, the independent start the engine of use motor M G1; Two schemes guarantees the reliability of engine starting process;
(6) this bimodulus structure can be so that under pure electronic operating mode, control B0 locking sun wheel s2 realizes the independent pure electric operation of motor M G1 and double-motor is combined pure electric operation, controls C1 coupling sun wheel s1 and sun wheel s2 and realizes the independent pure electric operation of motor M G2;
(7) this bimodulus structure can realize motor M G1 and engine combined power operation so that under hybrid power operating mode, motor M G2 and engine combined power operation, and double-motor associating and engine combined power operation;
(8) by control clutch C1 and C2, make system form multiple-working mode, can reduce the requirement to the rotating speed of motor and torque, reduced the processing and manufacturing difficulty of motor;
(9) adopt double-motor to carry out speed control, there is more degree of freedom, can make driving engine always work in best efficiency band;
(10) utilize power-transfer clutch B1 to control motor M G1 locking, and drg B0 carries out locking to sun wheel s2, can reduce waste of power, improved the efficiency of system;
(11) by lock-up clutch C2 make motor M G1 and driving engine constant speed synchronous, can improve the efficiency of system.
(12) by control clutch C1 and power-transfer clutch C2 while locking, can make the synchronization of output shaft, double-motor and driving engine, simplify mode.
compare with technology, advantage of the present invention is:
1, bimodulus two-stage satellite gear hybrid transmissions utilizes B1 to control electrical generator MG1 locking, and utilize B0 to control sun wheel s2 locking, improved the whole efficiency of system, and Prius can not carry out locking to electrical generator MG1, all the time have the conversion of energy, system effectiveness reduces;
2, bimodulus two-stage satellite gear hybrid transmissions can be realized multiple-working mode, can reduce the rotating speed of motor and torque request and the requirement to motor technology, and its direct effect is the processing and manufacturing difficulty that has reduced motor.
Accompanying drawing explanation
Fig. 1 is Toyota Prius hybrid transmissions constructional drawing.
Fig. 2 is bimodulus two-stage satellite gear hybrid transmissions constructional drawing of the present invention.
The specific embodiment
Be illustrated in figure 2 bimodulus two-stage satellite gear hybrid transmissions constructional drawing.This device by external toothing r1, the sun wheel s1 of driving engine (Engine), torsional vibration damper, motor M G1, motor M G2, drg B0, drg B1, liquid clutch C1, liquid clutch C2, first row planet row, the shared pinion carrier C of external toothing r2, the sun wheel s2 of the second planet row, two planet rows, main reduction gear, diff etc. parts form.Driving engine (Engine), torsional vibration damper, motor M G1, motor M G2 is as described below with the driven off by shaft annexation of double planet wheel rows of mixing five with diff: driving engine (Engine) is connected with the external toothing r1 of first planet row, motor M G2 is connected with the sun wheel s1 of first planet row, sun wheel s1 is connected with sun wheel s2 by controlling the closure of liquid clutch C1, the external toothing r2 of second planet row is connected with diff, the motor M G1 pinion carrier C shared with double planet wheel rows of mixing is connected, pinion carrier is connected with external toothing r1 by controlling the closure of liquid clutch C2, drg B0 can locking sun wheel s2 under some operating mode, drg B1 can locking pinion carrier C under some operating mode, intermeshing with the second stage satellite gear of external toothing engagement separately in two planet rows.
The mode of operation of driving device of the present invention:
By the mode of operation that hybrid vehicle is different, the mode of operation of this scheme is described:
(1) engine starting: when engine starting, according to the difference of operating mode, can use motor M G1 start the engine, now by power-transfer clutch C2 the be coupled exclusive gear ring r1 of the first planet and pinion carrier C, make the first planet row sun wheel s1, the exclusive gear ring r1 of the first planet and pinion carrier C synchronization, motor M G1 rotates and output torque, and power passes to driving engine by pinion carrier C, the exclusive gear ring r1 of the first planet, drives engine starting; Also can use motor M G2 start the engine, now by drg B1 locking pinion carrier C, motor M G2 rotates and output torque, and power passes to driving engine by the first planet row sun wheel s1, the exclusive gear ring r1 of the first planet, drives engine starting.Two schemes guarantees the reliability of engine starting process;
(2) electric-only mode operation: this driving device can be realized the pure electric operation of motor M G1, the pure electric operation of motor M G2, and double-motor is combined pure electric operation.During the pure electric operation of motor M G1, engine off because self towing astern torsional interaction remains static, drg B0 locking the second planet row sun wheel s2, motor M G1 rotates, power passes to wheel by pinion carrier C, the second planet row external toothing r2, diff, motor M G2 idle running; During the pure electric operation of motor M G2, engine off is static, power-transfer clutch C1 be coupled the first planet row sun wheel s1 and the second planet row sun wheel s2, make both synchronization, motor M G2 rotates, power passes to wheel by the first planet row sun wheel s1, the second planet row sun wheel s2, the second planet row external toothing r2, diff, motor M G1 idle running; Double-motor associating is pure when electronic, and motor M G1 and motor M G2 simultaneously output torque act on the second planet row external toothing r2, drive vehicle wheel rotation.
(3) hybrid mode operation: under hybrid power low-speed mode, engine starting, drg B0 locking the second planet row sun wheel s2, power-transfer clutch C2 the be coupled exclusive gear ring r1 of the first planet and pinion carrier C, make the first planet row sun wheel s1, the exclusive gear ring r1 of the first planet and pinion carrier C synchronization, the power of driving engine is by the exclusive gear ring r1 of the first planet, pinion carrier C, the second planet row external toothing r2, diff passes to wheel, by regulating the moment of torsion of motor M G1 and MG2, output shaft rotating speed is increased, and the moment of torsion of a part of driving engine is passed to motor M G2 generating, charge a battery, thereby make engine operation in ideal zone, improve system effectiveness, under hybrid power fast mode, drg B0 opens, power-transfer clutch C1 and C2 be locking simultaneously, make the first planet row sun wheel s1, the exclusive gear ring r1 of the first planet, the second planet row sun wheel s2, the second planet row external toothing r2 and pinion carrier C synchronization, now motor M G1 and motor M G2 do auxiliary power, keep the high-speed cruising of automobile together with driving engine.
Claims (2)
1. a bimodulus two-stage satellite gear hybrid transmissions, comprise driving engine, the first motor, the second motor, pinion carrier and diff, it is characterized in that: in described pinion carrier, be provided with the first planet row and the second planet row, first order satellite gear and second stage satellite gear are drawn together in the first described planet package, the second described planet row also comprises first order satellite gear and second stage satellite gear, the first order satellite gear of the first described planet row and the engagement of the sun wheel of the first planet row, the second stage satellite gear of the first described planet row and the engagement of the external toothing of the first planet row, the first order satellite gear of the second described planet row and the engagement of the sun wheel of the second planet row, the second stage satellite gear of the second described planet row and the engagement of the external toothing of the second planet row, the second stage satellite gear of the second stage satellite gear of the first described planet row and the second described planet row also meshes, the external toothing of the first described planet row is connected with described driving engine, the second described motor is connected with the sun wheel of the first planet row, the sun wheel of the first described planet row is also connected with the sun wheel of the second planet row by the closure of the first liquid clutch, and the external toothing of the second described planet row is connected with described diff, the first described motor is connected with described pinion carrier, the closure of described pinion carrier by the second liquid clutch and the first planet row external toothing be connected.
2. bimodulus two-stage satellite gear hybrid transmissions according to claim 1, it is characterized in that: in described pinion carrier, be also provided with the first drg of this pinion carrier of locking, on the second described planet row, be also provided with the second brake of a locking second planet row sun wheel.
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| CN201210097446.1A CN102616127B (en) | 2012-04-06 | 2012-04-06 | Hybrid power transmission device of dual-mode two-stage planet wheel |
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| CN102616127B true CN102616127B (en) | 2014-10-15 |
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Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102815197B (en) * | 2012-08-24 | 2014-12-10 | 北京理工大学 | Rear-driven double-mode four-gear hybrid power transmission device |
| CN103085643B (en) * | 2012-12-31 | 2015-08-05 | 长城汽车股份有限公司 | Hybrid gearbox |
| US9809105B1 (en) * | 2016-11-14 | 2017-11-07 | Ford Global Technologies, Llc | Hybrid transaxle |
| CN107933287A (en) * | 2017-12-08 | 2018-04-20 | 广西玉柴机器股份有限公司 | A kind of double planet wheel rows of mixing twin shaft hybrid transmissions of shared external toothing |
| CN109203967B (en) * | 2018-11-14 | 2024-02-27 | 王延芸 | Hybrid power transmission device |
| JP2020082925A (en) * | 2018-11-20 | 2020-06-04 | トヨタ自動車株式会社 | Vehicular control apparatus |
| CN109318704B (en) * | 2018-12-11 | 2024-02-27 | 王延芸 | Electric drive transmission device |
| CN112406507B (en) * | 2020-10-29 | 2024-04-16 | 东风汽车集团有限公司 | Hybrid power driving method and device, power system, vehicle and related equipment |
| CN114508574A (en) * | 2022-02-23 | 2022-05-17 | 浙江吉利控股集团有限公司 | Double-planetary-row transmission and vehicle |
| CN114508576A (en) * | 2022-02-23 | 2022-05-17 | 浙江吉利控股集团有限公司 | Double-planetary-row transmission and vehicle |
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| DE19909424A1 (en) * | 1999-02-23 | 2000-08-24 | Peter Tenberge | Hybrid gearing for vehicle |
| CN101817305A (en) * | 2010-04-02 | 2010-09-01 | 中国汽车技术研究中心 | Hybrid power drive device |
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Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP3641265B2 (en) * | 2002-12-04 | 2005-04-20 | 日産自動車株式会社 | Hybrid transmission |
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- 2012-04-06 CN CN201210097446.1A patent/CN102616127B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19909424A1 (en) * | 1999-02-23 | 2000-08-24 | Peter Tenberge | Hybrid gearing for vehicle |
| CN101992679A (en) * | 2009-08-24 | 2011-03-30 | 上海华普国润汽车有限公司 | Double planetary row four-axis hybrid power transmission device |
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| CN102312966A (en) * | 2011-08-23 | 2012-01-11 | 南京航空航天大学 | Double-planetary-gear-set double-mode hybrid power transmission device |
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