CN201045014Y - Hybrid electric vehicle motor-planetary gear integral driving system - Google Patents

Hybrid electric vehicle motor-planetary gear integral driving system Download PDF

Info

Publication number
CN201045014Y
CN201045014Y CNU200620098570XU CN200620098570U CN201045014Y CN 201045014 Y CN201045014 Y CN 201045014Y CN U200620098570X U CNU200620098570X U CN U200620098570XU CN 200620098570 U CN200620098570 U CN 200620098570U CN 201045014 Y CN201045014 Y CN 201045014Y
Authority
CN
China
Prior art keywords
motor
speed
planetary
gear
power
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CNU200620098570XU
Other languages
Chinese (zh)
Inventor
王亮
Original Assignee
王亮
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 王亮 filed Critical 王亮
Priority to CNU200620098570XU priority Critical patent/CN201045014Y/en
Application granted granted Critical
Publication of CN201045014Y publication Critical patent/CN201045014Y/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Abstract

In a motor and planetary-gear integral driving device which is connected to the rear of a car clutch, the motor is connected with a sun wheel of a second planetary-gear system, an inner tooth-ring of the sun wheel is fixed on a casing, and the second planetary-gear system only has the effect of speed reducing. A planetary frame of the second planetary-gear system is connected with an inner tooth-ring of a first planetary-gear system, an output shaft of the second planetary-gear system is connected with the sun wheel of the first planetary-gear system, and power is outputted by the planetary frame of the first planetary-gear system. The output shaft and a motor shaft are respectively provided with a brake of which the casing is connected with an outer casing of the driving device. Hybrid vehicles can be classified into a low speed working condition with the working of the motor, a middle speed working condition with the working of an engine and a high speed working condition with the combination working of the engine and the motor according to vehicular speed. Vehicle wheels brakes when the vehicle is stopped, and thereby ensuring the engine to drive the motor which is capable of generating power and charging the power to a battery.

Description

Motor of hybrid power automobile-planetary wheel integral drive system
Affiliated technical field
The utility model relates to a kind of motor of hybrid power automobile-planetary wheel integral drive system.
Background technology
At present, domestic known parallel type hybrid dynamic automobile adopts the change-speed box accessory drives, and motor is linked to each other by gear transmission with transmission countershaft.Though this layout has been continued to use traditional change-speed box, it is good to make inheritance, and structure is huge; Owing to increased the rotor inertia of change-speed box mechanical gear shift secondary part, need automatically controlled automatic mechanical type gear shift (AMT), cause the fault rate height; And the change speed gear box rigidity is limited, causes accessory drives gear mesh poor quality, the failure rate of machinery height.
Abroad with the hybrid electric drive system of epicyclic gear transmission, general gear is more, with high content of technology.But between rotating motion part, arrange the power-transfer clutch of rotation therewith, must on axle, bore control oil duct and oilhole, need many group oil sealing sealings, the big cost height of manufacture difficulty.
Summary of the invention
In order to overcome the deficiency of hybrid vehicle driving mechanism aspect such as rotary clutch in accessory drives, AMT gear shift or epicyclic gear transmission, the utility model provides a kind of mixed power automobile driving system, and it is made up of motor-planetary wheel packaged drive, parameter matching and control policy.
The technical scheme that the utility model adopted is: hardware aspect is to connect motor-planetary wheel packaged drive in the autoclutch back.In this device, motor is connected with the sun wheel of second planetary gear train, and on the housing that its internally toothed annulus is fixed, this planetary gear train only plays deceleration effort, and its pinion carrier links to each other with the internally toothed annulus of first planetary gear train; Input shaft is connected with the sun wheel of first planetary gear train; Power is by the pinion carrier output of first planetary gear train.Arrange a drg on input shaft and motor shaft respectively, brake casing links to each other with the actuating device shell.
Hybrid vehicle of the present utility model is divided into low regime, middling speed district and high velocity by the speed of a motor vehicle: input shaft is braked by drg, machine operation is slowed down through second planetary gear train, power is slowed down by pinion carrier output through first planetary gear train again, constitute the low speed of a motor vehicle operating mode of machine operation; Motor shaft is braked by drg, made engine power reach the first planetary gear train sun wheel, by pinion carrier output, constitute speed of a motor vehicle operating mode in the engine operation behind the dynamic retarding through input shaft; Two drgs are all discharged, and driving engine and motor are united participation motion output, constitute the high speed of a motor vehicle operating mode of associated working.
Implement the utility model, except that the hardware condition of motor-planetary wheel packaged drive structural arrangement, the parameter that also must match aspect software is selected and rational control policy, can prove effective.Parameter matching of the present utility model and control policy are narrated in the specific embodiment.
This shows that driving device structure compactness of the present utility model does not need AMT, do not have the power-transfer clutch of motion, thus it have simple in structure, in light weight, good reliability, advantage such as cost easy to manufacture is low, fuel-economizing is functional.
Description of drawings
Below in conjunction with drawings and Examples the utility model is further specified.
Fig. 1 is an arrangement plan of the present utility model.
Fig. 2 is the actuating device schematic diagram.
Fig. 3 is the planetary gear train arrangement plan.
Fig. 4 is the engine power characteristic map.
Fig. 5 is the motor power characteristic map.
Fig. 6 is hybrid vehicle drive performance figure.
1. input shafts among the figure, 2. housing, 3. brake disc, 4. brake clamp, the 5. first planet circular system internally toothed annulus, 6. first satellite gear, 7. first pinion carrier, 8. brake clamp, 9. second satellite gear, 10. brake disc, 11. motor stator, 12. rotors, 13. output shafts, 14. drive axles; E is a driving engine, and M is a motor, and C is a power-transfer clutch; C1, C2 are drg; 1,2 is first, second planetary gear train.
The specific embodiment
In Fig. 1, actuating device of the present utility model directly is connected on after the engine clucht, and the front end of input shaft 1 is connected with the clutch driven disk spline, and inserts in the bearing of engine crankshaft rear end.The housing 2 of actuating device links to each other with clutch-bell cover, and motor stator 11 is arranged in the housing, and the axle of rotor 12 links to each other with the sun wheel of second planetary gear train, and motor shaft is that hollow is through, and output shaft 13 passes through in rotor axis of electric.
Fig. 2 is the actuating device schematic diagram, and rotor 12 is connected with the second planetary wheel sun wheel, and on the fixing housing 2 of this planetary gear train internally toothed annulus, so this planetary gear train only plays deceleration effort, and pinion carrier links to each other with the first planetary gear train internally toothed annulus 5; Input shaft 1 is connected with the first planetary gear train sun wheel; Power is spread out of by the first planetary gear train pinion carrier 7.Arrange drg C1 and C2 on input shaft 1 and motor shaft respectively, brake disc 3 links to each other with input shaft 1, and brake disc 10 links to each other with motor shaft; Brake clamp 4 links to each other with actuating device shell 2 respectively with 8 housing, therefore can play brake action to input shaft 1 and motor shaft respectively.
When drg C1 braking, drg C2 are the low speed of a motor vehicle operating mode of machine operation when discharging.Motor torque drives the second planetary gear train sun wheel by motor shaft, slows down through second satellite gear 9, and transmission of power is to the first satellite gear internally toothed annulus 5; Because input shaft 1 is braking mode, first satellite gear 6 slows down first pinion carrier 7 again, is delivered to output shaft 13 again.This operating mode makes full use of the characteristic of motor low speed high torque, and through twice deceleration, so vehicle is in low speed driving; This moment, the propulsive effort of vehicle was big, and vehicle acceleration is also big.
Drg C2 braking, drg C1 are speed of a motor vehicle operating mode in the engine operation when discharging.Because the motor shaft braking, second satellite gear 9 can not rotate, and the first planet circular system internally toothed annulus 5 is braking mode; Engine power is slowed down transmission of power to first pinion carrier 7, by output shaft 13 outputs through first satellite gear 6 by input shaft 1; Because first satellite gear slows down, so the output torque increase, can guarantee that vehicle has bigger propulsive effort.This operating mode speed of a motor vehicle is a vehicle ' moderate speed range commonly used, as 40km/h to 50km/h, will guarantee that therefore driving engine always is in low oil consumption work down.
Drg C1, C2 all discharge, and this moment, driving engine and motor were united participation work, and first satellite gear 6 is subjected to the driving of uniting of driving engine and motor.It unites the condition that drives establishment; First satellite gear 6 with reach by driving engine circumferential force that input shaft 1 sun wheel is meshed and with reach the circumferential force that the first satellite gear internally toothed annulus 5 is meshed by motor and equate.Rotating speed when this moment, driving engine was in maximum power, as long as the control rotating speed of motor, motor torque adapts to the level of torque of driving engine automatically, just can satisfy the condition of associating driving.All not have increase with the circumferential force of its ingear any a pair of gear mesh concerning first satellite gear 6 this moment, therefore not variation of first pinion carrier, 7 output torques; And the central speed of first satellite gear is the speed sum that driving engine and motor are done the time spent separately, the speed of a motor vehicle sum of converting when promptly Ci Shi the speed of a motor vehicle is driving engine and motor independent drive.Because driving engine maintains max-power-output speed, and motor speed is adjustable, the rotating speed recruitment of first pinion carrier 7 is also adjustable with motor speed, and this moment, the recruitment of the speed of a motor vehicle was adjustable with motor speed.Therefore this hybrid power is not the torque stack, but the rotating speed stack.The high speed of a motor vehicle in vehicle place is travelled under this operating mode.
Fig. 3 is the planetary wheel arrangement plan, calculates the transmitting ratio of this device by this figure.
R1___ input shaft 1 sun wheel pitch radius
R2___ first satellite gear 6 pitch radiuss
The sun wheel pitch radius that r3___ links to each other with rotor axis of electric 12
R4___ second satellite gear 9 pitch radiuss
When drg C1 braking, drg C2 release, the transmitting ratio im of motor shaft 12 rotation speed n m and output shaft 13 rotation speed n d is
i m = n m n d = 4 ( r 1 + r 2 ) ( r 3 + r 4 ) r 3 ( r 1 + 2 r 2 )
When drg C2 braking, drg C1 release, the transmitting ratio ie of driving engine input shaft 1 rotation speed n e and output shaft 13 rotating speeds is
i e = n e n d = 2 ( r 1 + r 2 ) r 1
The rational Match of drive system parameters is another key of the present utility model.
As seen from Figure 4, the oil-efficient work area of driving engine be positioned at external characteristic power curve P 85% near, and range of speed is between peak torque speed n1 and max-power-output speed n2, so its oil-efficient torque characteristics is 85% of total external characteristics torque curve T, is the T1 characteristic.When driving engine was worked beyond the T1 characteristic line, the oil consumption meeting of driving engine increased a lot, therefore should control driving engine and always be on this characteristic line and work.
As seen from Figure 5, motor characteristic is permanent torque Tm when rotation speed n<nm1, and it is linear that power P m is; When rotation speed n m1<n<nm2, be permanent power P m, torque Tm is hyperbola.In the omnidistance operating range of motor, electromechanical conversion efficiency is all higher and differ less, so control policy allows motor to work under whole process.
In engine operation in the speed of a motor vehicle operating mode transient process, the speed of a motor vehicle should seamless link in the low speed of a motor vehicle operating mode of machine operation, drive steadily when operating mode is transformed, so motor maximum speed of revolution nm2 and driving engine peak torque speed n1 should have following relation
n 1 n m 2 ≤ r 3 ( r 1 + 2 r 2 ) 2 r 1 ( r 3 + r 4 )
"<" in the following formula makes the low speed of a motor vehicle operating mode of machine operation certain speed of a motor vehicle overlap ratio be arranged during the transition of speed of a motor vehicle operating mode in engine operation, guarantees the seamless smooth transition of the speed of a motor vehicle.
Running at high speed be, motor and driving engine are united driving, by the stress balance of first satellite gear 6, can draw the minimum torque Tmo of motor and the pass of the torque Tp of the fuel-efficient characteristic T1 of driving engine when max-power-output speed and are
Tmo Tp = 2 ( r 3 + r 4 ) r 1 r 3 ( r 1 + 2 r 2 )
Reversal development does not take place greater than Tmo to guarantee motor in the torque Tm that should make the motor maximum speed of revolution when uniting driving.
By determining the amount of capacity of driving engine and motor and the relation of rotating speed with co-relation.
Fig. 6 is hybrid vehicle drive performance figure, and ordinate F is a propulsive effort, and abscissa V is the speed of a motor vehicle.Low speed segment is the machine operation section, and the middling speed section is the engine operation section, and high regime is driving engine-motor associated working section.The automobile curve of resistance is f1 at the level road state, and the road resistance coefficient is 0.014; The automobile curve of resistance is f2 in that sloping state is arranged, and the road resistance coefficient is 0.1.The speed of a motor vehicle makes the automobile curve of resistance begin to raise up owing to the automobile air resistance begins to increase during greater than 50km/h.
The low speed segment propulsive effort is determined by motor characteristic, because the motor low speed high torque, and through actuating device secondary speed-reducing increase torque, so vehicle has bigger acceleration/accel; Middling speed section propulsive effort is determined that by the fuel-efficient characteristic of driving engine because middling speed section running time is the longest, driving engine is under the fuel-efficient characteristic works, and this moment, vehicle possessed bigger dynamic factor, can make vehicle acceleration or motor and be in generating state to battery charge; High regime is driving engine-motor associated working, because the stress balance of first satellite gear 6, propulsive effort still remains on the size of middling speed section when just having finished the fuel-efficient torque of driving engine, so propulsive effort no longer increases, and does not also reduce; But this moment, motor speed was adjustable, and the rotating speed recruitment of first pinion carrier 7 is determined that by motor speed this moment, the recruitment of the speed of a motor vehicle was stepless adjustable with motor speed, and battery is in discharge regime.
For low regime propulsive effort when the transition of middling speed district is not undergone mutation, realize that the propulsive effort transition is steady, can make
P m=P n1
The Pm___ motor rated power
The power of the fuel-efficient characteristic T1 of Pn1___ driving engine when peak torque speed
When vehicle is in when driving at moderate speed for a long time, battery charge state SOC constantly increases, when SOC surpasses limit value, the control engine speed descends, controlling motor simultaneously unites participation work and regulates its rotating speed, first satellite gear 6 of actuating device makes vehicle keep original residing driving at moderate speed both combinations of moving; Because this moment, motor was electric motor state, SOC descends thereupon.
The motor counter-rotating can realize reversing under electric-only mode.
Brake wheel when vehicle stops, releasing the brake C1 and C2 can make the engine drive electric power generation to battery charge.

Claims (2)

1. the motor of a hybrid vehicle-planetary wheel integral drive system, its rotor (12) is connected with the sun wheel of second planet circular system, the second planet circular system internally toothed annulus is fixed on the housing (2), second satellite gear (9) links to each other with the first planet circular system internally toothed annulus (5), drg (C1) and drg (C2) are housed respectively on input shaft (1) and the rotor (12), it is characterized in that the power of the power of input shaft (1) and rotor (12) all passes through first satellite gear (6) and is passed to output shaft (13).
2. the motor of hybrid vehicle according to claim 1-planetary wheel integral drive system is characterized in that; Drg (C1) links to each other with housing (2) with brake clamp (8) by brake clamp (4) respectively with drg (C2).
CNU200620098570XU 2006-08-21 2006-08-21 Hybrid electric vehicle motor-planetary gear integral driving system Expired - Fee Related CN201045014Y (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CNU200620098570XU CN201045014Y (en) 2006-08-21 2006-08-21 Hybrid electric vehicle motor-planetary gear integral driving system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CNU200620098570XU CN201045014Y (en) 2006-08-21 2006-08-21 Hybrid electric vehicle motor-planetary gear integral driving system

Publications (1)

Publication Number Publication Date
CN201045014Y true CN201045014Y (en) 2008-04-09

Family

ID=39308489

Family Applications (1)

Application Number Title Priority Date Filing Date
CNU200620098570XU Expired - Fee Related CN201045014Y (en) 2006-08-21 2006-08-21 Hybrid electric vehicle motor-planetary gear integral driving system

Country Status (1)

Country Link
CN (1) CN201045014Y (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011022939A1 (en) * 2009-08-24 2011-03-03 上海华普国润汽车有限公司 Brake control device for power system of hybrid electric vehicle
CN102029889A (en) * 2010-12-13 2011-04-27 镇江海普电子科技有限责任公司 Hybrid power transmission mechanism for driving clutch to be separated and combined, and gear shifting method
CN103009995A (en) * 2012-12-17 2013-04-03 华南理工大学 Power integration transmission mechanism
CN106114193A (en) * 2016-07-29 2016-11-16 重庆青山工业有限责任公司 A kind of hybrid power automobile driving system

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011022939A1 (en) * 2009-08-24 2011-03-03 上海华普国润汽车有限公司 Brake control device for power system of hybrid electric vehicle
CN102029889A (en) * 2010-12-13 2011-04-27 镇江海普电子科技有限责任公司 Hybrid power transmission mechanism for driving clutch to be separated and combined, and gear shifting method
CN102029889B (en) * 2010-12-13 2012-12-26 镇江海普电子科技有限责任公司 Hybrid power transmission mechanism for driving clutch to be separated and combined, and gear shifting method
CN103009995A (en) * 2012-12-17 2013-04-03 华南理工大学 Power integration transmission mechanism
CN103009995B (en) * 2012-12-17 2015-09-16 华南理工大学 A kind of Integrated power transmission device
CN106114193A (en) * 2016-07-29 2016-11-16 重庆青山工业有限责任公司 A kind of hybrid power automobile driving system
CN106114193B (en) * 2016-07-29 2018-06-19 重庆青山工业有限责任公司 A kind of hybrid power automobile driving system

Similar Documents

Publication Publication Date Title
CN102862470B (en) The multiple mode power shunting dynamical system of electric vehicle
CN102815198B (en) Mixed power automobile driving system based on variable transmission
CN102085795A (en) Hybrid driving system of vehicle clutch and power coupling synchronizer combined gear shift
CN201736790U (en) Actuating device for hybrid electric vehicle
WO2018137421A1 (en) Horizontal drive assembly of dual power source vehicle
US20100304920A1 (en) Hybrid Assembly , A Hybrid Power-Train , And A Method For Operating A Selectively Movable Assembly
CN102009590A (en) Electric stepless speed changer with three-gear speed change function and power drive mode thereof
CN207809033U (en) Hybrid electric drive system and vehicle
CN1778587A (en) Driving system of mixed dynamic vehicle
CN201633523U (en) Hybrid-power driving system
CN101204920A (en) Mixed motor vehicle driving system
CN104924889A (en) Hybrid power system, hybrid power vehicle and hybrid driving method
CN201322084Y (en) Integrative electrical variable transmission based on planetary gear two-gear speed-change mechanism
CN106523629A (en) Transversely-arranged vehicle driving assembly provided with double power sources
CN201045014Y (en) Hybrid electric vehicle motor-planetary gear integral driving system
CN104890496A (en) Hybrid power system, hybrid power vehicle and hybrid driving method
CN207809039U (en) Hybrid electric drive system and vehicle
CN205601595U (en) Vehicle hybrid synergy drive system and hybrid vehicle
CN205395752U (en) Parallel hybrid actuating system and car
CN204774601U (en) Hybrid power system and hybrid vehicle who has this system
CN111055669A (en) Automobile hybrid power driving device and automobile
CN108638852B (en) Electric automobile power system and efficiency improving method thereof
CN201045403Y (en) Mixed power vehicle double input planetary gear train
CN110303871A (en) A kind of multi gear hybrid power coupling mechanism, operational mode and its control strategy
CN207809041U (en) Hybrid electric drive system and vehicle

Legal Events

Date Code Title Description
C14 Grant of patent or utility model
GR01 Patent grant
C17 Cessation of patent right
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20080409

Termination date: 20100821