CN202944196U - Hybrid electric vehicle (HEV) dynamical system - Google Patents
Hybrid electric vehicle (HEV) dynamical system Download PDFInfo
- Publication number
- CN202944196U CN202944196U CN2012206206080U CN201220620608U CN202944196U CN 202944196 U CN202944196 U CN 202944196U CN 2012206206080 U CN2012206206080 U CN 2012206206080U CN 201220620608 U CN201220620608 U CN 201220620608U CN 202944196 U CN202944196 U CN 202944196U
- Authority
- CN
- China
- Prior art keywords
- clutch
- motor
- power
- drive motor
- battery
- 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
Links
Images
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
Landscapes
- Electric Propulsion And Braking For Vehicles (AREA)
Abstract
The utility model discloses a hybrid electric vehicle (HEV) dynamical system which aims to solve the problems that an (HEV) dynamical assembly in the prior art is large in size, large in occupied space of a whole system, incompact in structure and capable of bring difficulties for arranging of a whole vehicle. The system comprises an engine, a clutch, a drive motor, a speed reducer, a differential mechanism, a battery and a belt starter generator (BSG) motor, a clutch cover in the clutch is fixedly connected with an engine flywheel bolt in the engine, the right end of a sliding spline shaft of the clutch is fixedly connected with a motor input shaft of the drive motor through a first coupler, a motor output shaft of the drive motor is fixedly connected with an input shaft of the speed reducer through a third coupler, an output shaft of the speed reducer is fixedly connected with the left end of a drive gear input shaft of the differential mechanism through a second coupler, a wiring end of the drive motor is connected with the battery through wires, the BCG motor is connected with the battery (8) through wires, and the BCG motor is connected with the engine through belts. The HEV dynamical system is simple and compact in structure, and convenient to arrange.
Description
Technical field
The utility model relates to a kind of automobile dynamic system, and or rather, the utility model relates to a kind of hybrid power automobile power system.
Background technology
Along with the scarcity day by day of the energy and progressively giving prominence to of environmental problem, energy-conserving and environment-protective become a global important topic.And the potentiality of orthodox car aspect fuel-economizing and reduction discharging are limited, and electronlmobil is due to the restriction of battery technology, and cost is too high, continual mileage is too low, can not satisfy people's demand.Therefore have energy-saving and environmental protection, hybrid vehicle becomes the development tendency of auto-industry efficiently.
The basic configuration of hybrid vehicle has three kinds: tandem, parallel and series parallel type.Tandem configuration engine operation condition is independent of wheel and emission performance is good, but due to the secondary conversion that has energy, efficient is lower; And parallel configuration, engine efficiency is higher, and equipment is little, and cost is low, and still, driving engine and drive wheel mechanical connection, engine operation condition are affected by wheel.The series parallel type configuration has overcome tandem and parallel shortcoming and has combined their advantage, and larger advantage is comparatively speaking arranged.
Series-parallel hybrid electric system take the THS of Toyota as representative is volume production, and has obtained good benefit.The Pentium B70HEV of China's one vapour research and development and the Jim Press (Prius) of Toyota belong to strong mix-configuration together.Pentium B70HEV assembly adopts double-motor parallel-serial configuration (BSG+ISG+AMT+ single clutch).Due to strong mix-configuration hightech characteristic, Pentium B70HEV can realize all hybrid power functions, comprises tandem drive, parallel drive, series-parallel connection driving, driving engine driving separately, idle stop, Associated brake and regenerative brake etc.The application of Technology of Hybrid Electric Vehicle makes the oil consumption of Pentium B70HEV reach the level of 6.0L/100km, and the fuel-economizing of relatively similar traditional combustion engine automatic transmission car up to 42.8%, is 31.8% than manual car fuel saving ratio.Simultaneously, also there has been a series of scheme in China for the series parallel type configuration.China Patent Publication No. is CN1420034A, and open day is on May 28th, 2003, and denomination of invention is " power system of double-motor hybrid-power automobile ", discloses a kind of power system of double-motor hybrid-power automobile in this invention.Its characteristics have been two motors of major-minor, and the rotor shaft of main motor is connected with the output shaft of change speed gear box, and the rotor shaft of auxiliary-motor is connected with the bent axle of combustion engine; Major-minor motor and battery electrically connect.China Patent Publication No. is CN 101152837A, and open day is on April 2nd, 2008, and denomination of invention is " drive apparatus for hybrid vehicle ".This invention comprises driving engine, starter-generator, power-transfer clutch, speed-changing mechanism, dynamotor and closed-centre system.The Chinese utility model patent notification number is CN202080111U, the day for announcing is on December 21st, 2011, the utility model patent name is called " balanced type parallel-series hybrid power system ", and this utility model comprises BSG motor, main motor, change speed gear box, power-transfer clutch, driving engine, power accumulator etc.These three kinds of schemes all have two motors and a transmission system, and the dynamic assembly structural volume is large.Other patents such as China Patent Publication No. are CN 1919632A, open day is on February 28th, 2007, denomination of invention is that " novel double-motor parallel-serial hybrid power assembly ", China Patent Publication No. are CN101462482A, in open day on June 24th, 2009, denomination of invention also all comprises two motors and a change-speed box for " novel double-motor parallel-serial hybrid power assembly " configuration.To sum up tell, the series parallel type hybrid plan of domestic proposition has two motors and a change-speed box mostly.The space that the dynamic assembly volume is large, whole system takies is large, structure is not compact, has brought difficulty to arrangement.
Summary of the invention
Technical problem to be solved in the utility model is to have overcome prior art to have that the dynamic assembly volume is large, whole system takies space is large and structure is not compact, has brought hard problem to arrangement, and a kind of hybrid power automobile power system is provided.
For solving the problems of the technologies described above, the utility model is to adopt following technical scheme to realize: described hybrid power automobile power system comprises driving engine, drive motor, diff, power-transfer clutch, speed reduction gearing, battery and BSG motor.
clutch cover back plate in power-transfer clutch is captiveed joint with the engine flywheel bolt in driving engine, the right-hand member of the free-sliding spline axle in power-transfer clutch adopts No. 1 coupler to captive joint with the motor input shaft of drive motor, the motor output shaft of drive motor adopts No. 3 coupler to captive joint with the speed reduction gearing input shaft, the left end of the diff driving gear input shaft in reduction unit output shaft and diff adopts No. 2 coupler to captive joint, the terminals of drive motor are connected with battery wire, the terminals of BSG motor are connected with battery wire, adopt belt to be connected between BSG motor and driving engine.
The rotation axis conllinear of the engine flywheel described in technical scheme, free-sliding spline axle, motor input shaft, motor output shaft and speed reduction gearing input shaft.Reduction unit output shaft and diff driving gear input shaft rotation axis conllinear, the speed reduction gearing input shaft is parallel with the reduction unit output shaft rotation axis.
Power-transfer clutch described in technical scheme is electric control clutch open in usual, and it comprises clutch driven disc, clutch cover back plate, clutch center, clutch slip castellated shaft and clutch driving disc.Clutch center is positioned at the center of clutch driven disc, both rotation axis conllinear, clutch driven disc and clutch center riveted joint are fixing, the left end that clutch center is sleeved on the free-sliding spline axle is sliding block joint, clutch driving disc and clutch cover back plate be sleeved on successively the clutch driven disc right side the free-sliding spline axle around, the rotation axis conllinear of clutch center, free-sliding spline axle, clutch driving disc and clutch cover back plate.
Battery described in technical scheme is circumscribed with the charging unit that can use family expenses 220V power source charges.
Compared with prior art the beneficial effects of the utility model are:
1. hybrid power automobile power system described in the utility model has been cancelled change-speed box and distributing means for power supply, and hybrid power automobile power system is simple in structure, compact, arrangement convenience;
2. the battery described in hybrid power automobile power system described in the utility model has larger capacity.Thereby, when travelling, daily short distance can run on electric-only mode, and described battery has external charging unit, can use family expenses 220V power supply that battery is charged, what utilize is the electric energy that obtains from electrical network because daily short distance is travelled, and therefore, has reduced the cost of day-to-day operation;
3. satisfied respectively the dynamic property requirement when drive motor in hybrid power automobile power system described in the utility model and driving engine type selecting, the collaborative work of drive motor, driving engine BSG motor simultaneously, can improve the efficient of propulsion source, the automobile that therefore described hybrid power automobile power system is installed has excellent dynamic property and economy.
Description of drawings
Below in conjunction with accompanying drawing, the utility model is further described:
Fig. 1 is the schematic block diagram that hybrid power automobile power system structure described in the utility model forms;
Fig. 2 is the front view that hybrid power automobile power system structure described in the utility model forms;
Fig. 3 is that hybrid power automobile power system described in the utility model is at the power transmission line figure of associating drive pattern;
Fig. 4 is that hybrid power automobile power system described in the utility model is at the power transmission line figure of pure motor driving pattern;
Fig. 5 is that hybrid power automobile power system described in the utility model drives separately the also power transmission line figure of charge mode at driving engine;
Fig. 6 is that hybrid power automobile power system described in the utility model is at the power transmission line figure of tandem working pattern;
Fig. 7 is that hybrid power automobile power system described in the utility model is at the power transmission line figure of regenerative brake pattern;
Fig. 8 is the whole performance map of driving engine selected in hybrid power automobile power system described in the utility model;
Fig. 9 is the efficiency chart of drive motor selected in hybrid power automobile power system described in the utility model;
Figure 10 is the efficiency chart of BSG motor selected in hybrid power automobile power system described in the utility model;
in figure: 1. driving engine, 2. power-transfer clutch, 3. drive motor, 4. speed reduction gearing, 5. diff, 6. left half axle, 7. left wheel, 8. battery, 9.BSG motor, 10. engine flywheel, 11. clutch driven disc, 12. clutch cover back plate, 13. clutch center, 14.1 number coupler, 15. motor output shaft, 16. reduction unit output shaft, 17. diff driving gear input shaft, 18.2 number coupler, 19. speed reduction gearing big gear wheel, 20. speed reduction gearing miniature gears, 21. speed reduction gearing housing, 22. speed reduction gearing input shaft, 23.3 number coupler, 24. motor input shaft, 25. clutch slip castellated shaft, 26. clutch driving disc.
The specific embodiment
Below in conjunction with accompanying drawing, the utility model is explained in detail:
Consult Fig. 1, hybrid power automobile power system described in the utility model comprises driving engine 1, power-transfer clutch 2, drive motor 3, speed reduction gearing 4, diff 5, battery 8 and BSG motor 9.Wherein, the selection of driving engine 1, drive motor 3, speed reduction gearing 4, battery 8 and BSG motor 9 is all according to basic specification and the designing requirement of vehicle.Car load basic specification and vehicle performance require detailed description to consult table 1 and table 2:
Table 1 car load basic specification
The requirement of table 2 vehicle performance
| Performance requriements | Index |
| Maximum speed (km/h) | ≥120 |
| 0～100km/h pick-up time (s) | ≤12 |
| Max. climb slope | ≥30% |
| Electric-only mode continual mileage (km) | ≥50 |
| Improve the economy of vehicle | ≥30% |
With reference to car load basic specification and vehicle performance requirement, require to estimate respectively the demand power of propulsion source according to maximum speed, max. climb slope and acceleration capability.Calculation specifications such as following table:
Table 3 propulsion source calculation of parameter
1. driving engine type selecting
The result of calculation of table on foundation, selection is suitable for the driving engine of power system described in the utility model.
Consult Fig. 8, the engine petrol that the driving engine 1 in the utility model adopts automotive field generally to adopt.The peak power of this driving engine will satisfy acceleration capability and the grade climbing performance requirement of the vehicle that power system described in the utility model is installed.Calculate according to table 1, as follows with reference to the driving engine principal parameter that existing product is selected:
Table 4 driving engine basic specification
| Peak torque | 155Nm@3800rpm |
| Peak power | 77kw@5200rpm |
| Discharge capacity (ml) | 1590 |
| Idling (rpm) | 1000 |
| Maximum speed of revolution (rpm) | 6000 |
The universal characteristic of this driving engine as shown in Figure 8.
2. drive motor type selecting
The result of calculation of table on foundation, selection is suitable for the drive motor of power system described in the utility model.
Consult Fig. 9, the drive motor that the drive motor 3 in the utility model adopts pure electric automobile or field of hybrid electric vehicles generally to adopt.Drive motor 3 in the utility model is selected permagnetic synchronous motor.This motor two ends have respectively an input shaft and an output shaft, and input shaft and output shaft rotation axis conllinear.This motor rated power will satisfy the maximum speed requirement, and its peak torque all will satisfy acceleration capability and the grade climbing performance requirement of the vehicle that power system described in the utility model is installed.Calculate according to table 1, as follows with reference to the drive motor principal parameter that existing product is selected:
Table 5 drive motor basic specification
| Motor type (exchange/PM) | PM |
| Motor rated power (kW) | 43 |
| Motor torque rating (Nm) | 100 |
| Motor peak power (kW) | 90 |
| Motor peak torque (Nm) | 210 |
| Maximum speed of revolution (rpm) | 10000 |
| Minimum steady speed (rpm) | 500 |
The efficiency chart of drive motor as shown in Figure 9.
3.BSG choice of electrical machine
Consult Figure 10, the permagnetic synchronous motor that the BSG motor 9 in the utility model adopts field of hybrid electric vehicles generally to use; Namely should follow following two principles when BSG motor 9 type selecting:
1) its peak torque must can start the engine 1, make the operation point of driven by engine BSG motor 9 chargings drop in the efficient region of BSG motor 9 as far as possible;
2) vehicle operating that is arranged on power system described in the utility model is when series model, and BSG motor 9 will provide electric energy to drive motor.Therefore the power of the specified charging of BSG motor 9 should be greater than the average power of operating mode demand; Demand power under statistical computation NEDC operating mode, obtaining its average demand power is 15kw; With reference to the data of existing motor, the fuel oil consumption universal curve of while binding engine, BSG motor 9 basic specifications of selection are as follows:
Table 6BSG motor basic specification
| Motor type (exchange/PM) | PM |
| Motor rated power (kW) | 16 |
| Motor torque rating (Nm) | 72.5 |
| Maximum speed of revolution (rpm) | 8000 |
| Minimum steady speed (rpm) | 500 |
| Motor peak power (kW) | 32 |
| Motor peak torque (Nm) | 145 |
The efficiency chart of BSG motor as shown in Figure 10.
4. selection speed reduction gearing
The product that speed reduction gearing 4 in the utility model adopts pure electric automobile field or field of hybrid electric vehicles generally to adopt.The selection of the tradition ratio of speed reduction gearing 4 will make the range of speed of driving engine 1 and drive motor 3 satisfy the requirement that max. climb slope is also satisfied in its torque simultaneously of vehicle maximum speed and minimum stabilizing speed.Be calculated as follows:
Table 7 speed reduction gearing gear ratio calculation
According to above-mentioned result of calculation, speed reduction gearing reduction ratio i
1=2.36, because transmission is smaller, select single cylindrical gear reducer.
Consult Fig. 2, speed reduction gearing mainly is comprised of speed reduction gearing housing 21, speed reduction gearing input shaft 22, reduction unit output shaft 16, speed reduction gearing miniature gears 20, speed reduction gearing big gear wheel 19.This speed reduction gearing is realized deceleration by the one-level gear transmission.
5. selection battery
The power of the battery 8 in the utility model is greater than the peak power of drive motor 3 and BSG motor 9, thereby guarantees the normal operation of drive motor 3 and BSG motor 9; For guaranteeing that this motor vehicle driven by mixed power electric-only mode continual mileage satisfies daily travelled distance requirement, the capacity of this battery 8 otherwise less than the needed capacity of cell of its electric-only mode continual mileage.According to above selected propulsion source and parts, the incorporation engineering experience is built vehicle simulation model inside AVL Cruise software.When emulation under the NEDC operating mode, the hybrid vehicle of this configuration are travelled 50km at electric-only mode, the consumes power 24.5Ah of institute, effective loading capacity in power taking pond 8 is 0.8, therefore obtaining battery 8 capacity that the NEDC operating mode determines is 24.5Ah/0.8=30.6Ah.After rounding, determine that battery 8 capacity are decided to be 31Ah.Simultaneously, this battery 8 has the external charging unit of capacity of pure electric automobile or plug-in hybrid-power automobile use, can use the 220V power supply of family expenses to battery 8 chargings.
6. selection power-transfer clutch
Consult Fig. 2, power-transfer clutch 2 in the utility model adopts the normally open clutch that uses in certain automatic variable speed device for car machinery, with reference to the power-transfer clutch 2 in Fig. 2, power-transfer clutch 2 comprises clutch driven disc 11, clutch cover back plate 12, clutch center 13, clutch slip castellated shaft 25 and clutch driving disc 26; This normally disengaged clutch and traditional normally closed power-transfer clutch form and structure basically identical.Just compare with traditional normally closed power-transfer clutch, when the not start of normally open clutch actuating unit, there is no thrust between clutch driving disc 26 and clutch driven disc 11, have the gap between engine flywheel 10 and clutch driven disc 11, both separate for they.At this moment, power-transfer clutch 2 does not carry out transmission of power.When the start of normally open clutch actuating unit, produce thrust between clutch driving disc 26 and clutch driven disc 11, engine flywheel 10 and clutch driven disc 11 combinations, thus carry out transmission of power.
consult Fig. 1 and Fig. 2, adopt belt to be connected between the belt pulley of the belt pulley of BSG motor 9 and driving engine 1, driving engine 1 is captiveed joint with clutch cover back plate 12 bolts by engine flywheel 10, clutch center 13 is positioned at the center of clutch driven disc 11, both rotation axis conllinear, clutch driven disc 11 is fixing with clutch center 13 riveted joints, the splined hole of clutch center 13 centers and the left end sliding block joint of the free-sliding spline axle 25 in power-transfer clutch 2, be that the left end that clutch center 13 is sleeved on free-sliding spline axle 25 is sliding block joint, clutch driving disc 26 and clutch cover back plate 12 be sleeved on successively clutch driven disc 11 right sides free-sliding spline axle 25 around, clutch center 13, free-sliding spline axle 25, the rotation axis conllinear of clutch driving disc 26 and clutch cover back plate 12.The right side of free-sliding spline axle 25 (output) end is captiveed joint with the input shaft 24 of drive motor 3 by No. 1 coupler 14; The output shaft 15 of drive motor 3 is captiveed joint by No. 3 coupler 23 with speed reduction gearing input shaft 22; Reduction unit output shaft 16 is captiveed joint by No. 2 coupler 18 with the diff driving gear input shaft 17 in diff 5, and diff 5 is last is connected with left wheel with right axle shaft by left half axle 6 and is connected with right wheel.The rotation axis conllinear of engine flywheel 10, clutch driven disc 11, clutch center 13, free-sliding spline axle 25, drive motor input shaft 24 and drive motor output shaft 15, speed reduction gearing input shaft 22; Reduction unit output shaft 16 and diff driving gear input shaft 17 rotation axis conllinear.Speed reduction gearing input shaft 22 is parallel with reduction unit output shaft 16 rotation axiss.The terminals of drive motor 3 and battery 8 are electrically connected to, and the terminals of BSG motor 9 and battery 8 are electrically connected to.
The principle of work of described hybrid power automobile power system:
Consult Fig. 3 to Fig. 7, in figure, the parts of heavy line sign are the parts that present mode participates in transmission of power and energy transmission, and the heavy line arrow has shown the direction of transmission of power, and the fine line arrow has shown the direction of electrical energy transfer:
1. associating drive pattern:
Consult Fig. 3, BSG motor 9 is not worked, and driving engine 1 and drive motor 3 are worked simultaneously, and power-transfer clutch 2 is in bonding state, and drive motor 3 works in motoring condition.Driving engine 1 is connected with drive motor 3 by power-transfer clutch 2, carries out transmission of power, and drive motor 3 carries out transmission of power by speed reduction gearing 4, diff 5, left half axle 6, left wheel 7 and right axle shaft, right wheel simultaneously; Battery 8 provides electric energy for drive motor 3.
2. pure motor driving pattern:
Consult Fig. 4, BSG motor 9 and driving engine 1 are not all worked, and power-transfer clutch 2 is in released state, and drive motor 3 works in motoring condition.Drive motor 3 carries out transmission of power by speed reduction gearing 4, diff 5, left half axle 6 with left wheel 7 and right axle shaft, right wheel; Battery 8 provides electric energy for drive motor 3.
3. driving engine drives separately and charge mode:
Consult Fig. 5, BSG motor 9 is not worked, and driving engine 1 and drive motor 3 are worked simultaneously, and power-transfer clutch 2 is in bonding state, and drive motor 3 works in charge condition.Driving engine 1 is connected with drive motor 3 by power-transfer clutch 2, carries out transmission of power, and drive motor 3 carries out transmission of power by speed reduction gearing 4, diff 5, left half axle 6, left wheel 7 and right axle shaft, right wheel simultaneously; Drive motor 3 gives battery 8 chargings.
4. series model:
Consult Fig. 6, BSG motor 9, driving engine 1 and drive motor 3 are worked simultaneously, and power-transfer clutch 2 is in released state, and BSG motor 9 works in generating state, and drive motor 3 works in motoring condition.Driving engine 1 carries out transmission of power by belt and BSG motor 9; Drive motor 3 carries out transmission of power by speed reduction gearing 4, diff 5, left half axle 6, left wheel 7 and right axle shaft, right wheel; The required electric weight of drive motor 3 is directly provided by the electric weight that BSG motor 9 sends, and not enough is provided by battery 8.
5. regenerative brake pattern:
Consult Fig. 7, BSG motor 9 and driving engine 1 are not all worked, and power-transfer clutch 2 is in released state, and drive motor 3 works in generating state.Left wheel 7, left half axle 6 and right axle shaft, right wheel, diff 5, speed reduction gearing 4 carry out transmission of power with drive motor 3; Drive motor 3 gives battery 8 chargings.
The vehicle of equipping hybrid power system described in the utility model is plug-in hybrid-power automobile (PHEV, plug-in hybrid electric vehicle), consistent with other plug-in hybrid-power automobiles, its working process also can be divided into according to the consumption process of battery electric quantity CD(Charge Depleting) and two stages of CS (Charge Susta ining), namely battery electric quantity is depleted to the battery electric quantity threshold value SOC of a setting from 100% or higher value
CSThis stage be the CD stage, afterwards, it is the CS stage that battery electric quantity maintains the stage that certain limit fluctuates up and down.According to the power transmission line of above-mentioned each pattern, determine the control policy of each pattern and the switching condition between pattern in conjunction with the speed of a motor vehicle, SOC, demand torque, brake pedal signal and optimal curve of engine etc., the concrete variable-definition of using is as showing:
Table 8 control policy parameter list
Control policy and the switching condition between pattern of each pattern are as follows:
1) associating drive pattern
When vehicle operating in the CS stage, when climbing or anxious the acceleration, the torque of chaufeur demand is larger, battery electric quantity only rely on engine operation to be not enough to drive vehicle when optimal curve, if at this moment can also allow drive motor 3 participate in driving adopt the associating drive pattern to satisfy at this moment larger torque-demand.At this moment, control engine 1 works in the Optimum Economic curve, and driving engine 1 is operated in the part torque that is not enough to satisfy the chaufeur demand on this curve and is provided by drive motor 3:
Namely in the CS stage, if T
req＞T
optAnd OC
M＞SOC＞SOC
L:
T
e＝T
opt；T
m＝T
req-T
opt；T
mb＝0；
2) pure motor driving pattern
Vehicle operating is when the pure motor driving pattern, and its economy, ride comfort are better, and can realize zero-emission.Therefore, in the situation that battery 8 electric weight abundances should allow vehicle operating at electric-only mode.As previously described, make vehicle operating in electric-only mode during the stage at CD.In the CS stage, if braking energy take-back model, series model and driving engine drive separately when also power generation mode makes battery electric quantity rise highlyer, vehicle also will operate in the pure motor driving pattern.
Namely in the CD stage, if SOC＞SOC
CSPerhaps in the CS stage, if SOC＞SOC
M:
T
e＝0；T
m＝T
req；T
mb＝0；
3) driving engine drives separately and charge mode
In the CS stage, in the time of in and the range of speed of engine speed in engine operation that the speed of a motor vehicle is corresponding low when battery 8 electric weight, driving the required torque of vehicle is only provided by driving engine.At this moment, power-transfer clutch 2 keeps combination, and this hybrid power automobile controller control engine 1 torque makes on its optimal curve that is operated in driving engine 1 work.Driving engine 1 provides the driving cycle of vehicle required torque.Simultaneously, utilize the torque of having more than needed after the driving vehicle that battery 8 is charged by drive motor 3.
Namely in the CS stage, if SOC
L≤ SOC≤SOC
MAnd V
L＜V＜V
HAnd T
req＜T
opt:
T
e＝T
opt；T
m＝T
req-T
opt；T
mb＝0；
In addition, when the electric weight of battery 8 drops to when being not enough in drive motor and the range of speed of engine speed in engine operation corresponding to the speed of a motor vehicle, if chaufeur demand torque this moment is greater than torque corresponding to driving engine economic curve, vehicle will operate in driving engine and drive separately and power generation mode.At this moment driving engine provides and drives the required whole torques of vehicle.
SOC＜SOC even
LAnd V
L＜V＜V
HAnd T
rep〉=T
opt:
T
e＝T
req；T
m＝0；T
mb＝0；
4) tandem working pattern
In the CS stage, and driving engine 1 rotating speed that the speed of a motor vehicle corresponding low when battery 8 electric weight be not in the range of speed of driving engine 1 work the time, and driving engine 1 drives 9 generatings of BSG motor by belt, and drive motor 3 provides the driving vehicle required power.At this moment, control engine 1 rotating speed and torque are on driving engine 1 efficient work point, and driving engine 1 drives 9 generatings of BSG motor by belt.Drive motor 3 utilizes electricity energy driven vehicle that BSG motor 9 produces, simultaneously with power storage more than needed on 8 li, battery.
Namely in the CS stage, if SOC≤SOC
MAnd (V≤V
LOr V 〉=V
H) and T
req＜T
opt:
T
e＝T
shev；T
m＝T
req；T
mb＝T
shev；
5) regenerative brake pattern
During car brakeing, battery 8 underfill electricity and automobile do not stop and adopt the regenerative brake pattern to reclaim braking energy.During regenerative brake, the charging torque of motor is determined according to motor speed and brake pedal.At this moment power-transfer clutch 2 separates.Kinetic energy is delivered to drive motor 3 through wheel, semiaxis, diff, speed reduction gearing, by 8 chargings of 3 pairs of batteries of drive motor, realizes that braking energy reclaims.
SOC＜SOC even
HAnd V 〉=V
STOPAnd Break＞Break_pedal is:
T
e＝0；T
m＝T
REG；T
mb＝0；
6) idle stop pattern
During due to driving engine 1 low-speed running, emission behavior and economy are all bad, therefore will avoid driving engine 1 idling operation as far as possible.Parking of automobile and continuing for some time and demand torque when being zero kills engine 1, drive motor 3 and BSG motor 9.So just cancel traditional engine idle, realized the purpose of energy-saving and emission-reduction.Simultaneously, power-transfer clutch 2 disconnects, and disconnection driving engine 1 is connected with drive motor 3, speed reduction gearing 4.When vehicle launch, enter tandem working pattern or pure motor driving pattern according to battery 8 electric weight situations, vehicle is started fast.
V＜V even
STOPAnd TIME
STOP＞TIME
Stop01And T
req=0:
T
e＝0；T
m＝0；T
mb＝0；
Simulation results show:
Build the whole vehicle model that comprises hybrid power system described in the utility model in the AVL cruise of simulation software, build the control policy of this power system in Matlab Simulink, then associative simulation, hybrid vehicle (PHEV) simulation result such as the following table that obtain installing the hybrid power system that the utility model proposes:
Table 9 dynamics simulation result
Annotate: 1SOC＜SOC
CSThe time, vehicle runs on tandem working pattern, associating drive pattern and tandem working pattern successively under full load mode.2 choose+to the mark orthodox car, its principal parameter such as following table 10:
Table 10 pair mark orthodox car car load basic specification
By above-mentioned dynamics simulation result as can be known, the hybrid vehicle of the hybrid power system that installation the utility model proposes (PHEV), 0～100km/h pick-up time can reach 10.5s, max. climb slope can reach 54.8%, all be better than with to the target traditional vehicle, owing to there is no change-speed box, it is little that its maximum speed will be compared the target traditional vehicle, but, also satisfied the requirement of the maximum speed in the designing requirement.
According to simulation result, in conjunction with the average price of current 93# gasoline (7.7 yuan/L), and the residential electricity consumption average electricity price (0.53 yuan/kwh), obtain the following table data:
Table 11 economy simulation result
Can find out from emulated data, the hybrid vehicle that hybrid power system described in the utility model is installed has economy preferably.When daily short-haul trip (mileage is less than 50km), this hybrid vehicle runs on electric-only mode always, can realize zero-emission, has effectively improved daily economy of travelling.
Therefore, the hybrid power automobile power system that the utility model proposes has dynamic property and economy preferably.
Claims (4)
1. hybrid power automobile power system, comprise driving engine (1), drive motor (3) and diff (5), it is characterized in that, described hybrid power automobile power system also comprises power-transfer clutch (2), speed reduction gearing (4), battery (8) and BSG motor (9);
clutch cover back plate (12) in power-transfer clutch (2) is captiveed joint with engine flywheel (10) bolt in driving engine (1), the right-hand member of the free-sliding spline axle (25) in power-transfer clutch (2) adopts No. 1 coupler (14) to captive joint with the motor input shaft (24) of drive motor (3), the motor output shaft (15) of drive motor (3) adopts No. 3 coupler (23) to captive joint with speed reduction gearing input shaft (22), the left end of the diff driving gear input shaft (17) in reduction unit output shaft (16) and diff (5) adopts No. 2 coupler (18) to captive joint, the terminals of drive motor (3) are connected with battery (8) electric wire, the terminals of BSG motor (9) are connected with battery (8) electric wire, adopt belt to be connected between BSG motor (9) and driving engine (1).
2. according to hybrid power automobile power system claimed in claim 1, it is characterized in that the rotation axis conllinear of described engine flywheel (10), free-sliding spline axle (25), motor input shaft (24), motor output shaft (15) and speed reduction gearing input shaft (22); Reduction unit output shaft (16) and diff driving gear input shaft (17) rotation axis conllinear, speed reduction gearing input shaft (22) is parallel with reduction unit output shaft (16) rotation axis.
3. according to hybrid power automobile power system claimed in claim 1, it is characterized in that, described power-transfer clutch (2) is electric control clutch open in usual, and it comprises clutch driven disc (11), clutch cover back plate (12), clutch center (13), clutch slip castellated shaft (25) and clutch driving disc (26);
clutch center (13) is positioned at the center of clutch driven disc (11), both rotation axis conllinear, clutch driven disc (11) is fixing with clutch center (13) riveted joint, the left end that clutch center (13) is sleeved on free-sliding spline axle (25) is sliding block joint, clutch driving disc (26) and clutch cover back plate (12) be sleeved on successively clutch driven disc (11) right side free-sliding spline axle (25) around, clutch center (13), free-sliding spline axle (25), the rotation axis conllinear of clutch driving disc (26) and clutch cover back plate (12).
4. according to hybrid power automobile power system claimed in claim 1, it is characterized in that, described battery (8) is circumscribed with the charging unit that can use family expenses 220V power source charges.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012206206080U CN202944196U (en) | 2012-11-21 | 2012-11-21 | Hybrid electric vehicle (HEV) dynamical system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012206206080U CN202944196U (en) | 2012-11-21 | 2012-11-21 | Hybrid electric vehicle (HEV) dynamical system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202944196U true CN202944196U (en) | 2013-05-22 |
Family
ID=48419909
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012206206080U Expired - Fee Related CN202944196U (en) | 2012-11-21 | 2012-11-21 | Hybrid electric vehicle (HEV) dynamical system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202944196U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102935798A (en) * | 2012-11-21 | 2013-02-20 | 吉林大学 | Hybrid electric vehicle power system |
| CN104149776A (en) * | 2014-08-27 | 2014-11-19 | 安徽江淮汽车股份有限公司 | Hybrid power automobile system and control method thereof |
| CN108657159A (en) * | 2017-03-31 | 2018-10-16 | 比亚迪股份有限公司 | Hybrid vehicle and its dynamical system and electricity-generating control method |
-
2012
- 2012-11-21 CN CN2012206206080U patent/CN202944196U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102935798A (en) * | 2012-11-21 | 2013-02-20 | 吉林大学 | Hybrid electric vehicle power system |
| CN104149776A (en) * | 2014-08-27 | 2014-11-19 | 安徽江淮汽车股份有限公司 | Hybrid power automobile system and control method thereof |
| CN108657159A (en) * | 2017-03-31 | 2018-10-16 | 比亚迪股份有限公司 | Hybrid vehicle and its dynamical system and electricity-generating control method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102991331B (en) | Plug-in hybrid electric vehicle | |
| CN102085795B (en) | Hybrid driving system of vehicle clutch and power coupling synchronizer combined gear shift | |
| CN101920652B (en) | Series/parallel double-motor and multi-clutch hybrid drive unit for vehicle | |
| CN100421979C (en) | Power coupler for mixed power automobile | |
| CN102935798A (en) | Hybrid electric vehicle power system | |
| CN102259584B (en) | Hybrid power driven system and vehicle comprising same | |
| CN101898557B (en) | Control method of electric four-wheel drive hybrid vehicle | |
| CN102259580B (en) | Hybrid power transmission system | |
| CN102874092B (en) | A kind of range extended electric vehicle power system adopting two clutch two-speed transmission | |
| CN106240336B (en) | A kind of plug-in bi-motor four-wheel-drive hybrid power system and control method | |
| CN1420034A (en) | Power system of double-motor hybrid-power automobile | |
| CN102897017A (en) | Dynamic-coupling electric control power gear shift hybrid power system | |
| CN103204056A (en) | Hybrid power driving assembly | |
| CN106394548B (en) | A kind of vehicle layered coordination energy efficiency controlling method of Plug-in four-wheel-drive hybrid power | |
| CN102897016A (en) | Drive transmission and control system of double-clutch variable-speed four-wheel driven hybrid power vehicle | |
| CN201863701U (en) | Dual-motor hybrid power system | |
| CN205554179U (en) | Two separation and reunion series -parallel connection hybrid power system of unipolar | |
| CN202491672U (en) | Hybrid power drive system for four-wheel-driven hybrid vehicle | |
| CN202896270U (en) | Extend range type electric vehicle power system utilizing double-clutch two-gear transmission | |
| CN102874107A (en) | Extended range electromobile power system using dual-clutch transmission gear | |
| CN101920654A (en) | Novel double-motor and multi-clutch hybrid power system for vehicle | |
| CN202944196U (en) | Hybrid electric vehicle (HEV) dynamical system | |
| CN202283872U (en) | Multi-motor compound system for hybrid electric vehicle | |
| CN202200825U (en) | Plug-in hybrid passenger car driving system | |
| CN102358162A (en) | Hybrid oil-electricity energy-saving power device and control method thereof |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130522 Termination date: 20171121 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |