CN101108586B - Hybrid vehicle - Google Patents
Hybrid vehicle Download PDFInfo
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- CN101108586B CN101108586B CN2007101278122A CN200710127812A CN101108586B CN 101108586 B CN101108586 B CN 101108586B CN 2007101278122 A CN2007101278122 A CN 2007101278122A CN 200710127812 A CN200710127812 A CN 200710127812A CN 101108586 B CN101108586 B CN 101108586B
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- 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
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- 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
- Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
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- Electric Propulsion And Braking For Vehicles (AREA)
- Hybrid Electric Vehicles (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
The present invention provides a hybrid vehicle including a first transmission path that transmits a traction of an engine to driving wheels and a second transmission path that transmits a traction of a motor to the driving wheels, and the hybrid vehicle runs by alternatively selecting either the first or second transmission path or in combination thereof. The first transmission path has a first reduction gear ratio that is defined to be smaller than a reduction gear ratio at which a maximum vehicle speed can be achieved by the traction of the engine alone.
Description
Technical field
The present invention relates to a kind of motor vehicle driven by mixed power; The motor force of engine drive power of its combination engine (combustion engine) and electrical motor (motor) and going; Especially relate to a kind of motor vehicle driven by mixed power, it possesses second bang path that engine drive power is delivered to first bang path of drive wheel and motor force is delivered to drive wheel.
Background technology
At present; Well-known motor vehicle driven by mixed power does; Utilize driving engine and electrical motor propulsive effort characteristic separately, in the vehicle speed range of the not enough certain speed of vehicle (speed V 1), go through second bang path that motor force is delivered to drive wheel; In the vehicle speed range of speed V more than 1; And be delivered to first bang path of drive wheel and go with said second bang path with engine drive power, near maximum speed Vmax, the main use gone by engine-driven first bang path.In this motor vehicle driven by mixed power; The mode that becomes the characteristic that can cover maximum speed Vmax with the engine drive force characteristic is confirmed the ratio of number of teeth of said first bang path; Because of not being set in second bang path and first bang path, oversimplifies by the variable-speed motor with variable gears; And near maximum speed Vmax, engine drive power is delivered to drive wheel and goes (with reference to special permission document 1) by first bang path.
Special permission document 1: specially permit No. 2942533 communique (with reference to paragraph 0015～0028, and Fig. 1, Fig. 2).
But; In the structure of said special permission document 1 disclosed motor vehicle driven by mixed power; When underload cruising (go the rounds); Utilizing generator for electricity generation and to go through the series running pattern of direct motor drive drive wheel, or, use first bang path that comprises bigger (the low coefficient ratio of number of teeth) driving device of the reduction ratio set in order to utilize engine drive power to realize maximum speed Vmax and utilize the engine drive Lixing to sail.
But, under series model,, possibly have the problem of the fuel consumption rate decline of vehicle because the transmission efficiency of propulsive effort reduces.In addition; When only going by engine drive via first bang path of the driving device of the ratio of number of teeth that comprises low coefficient; Low coefficient ratio of number of teeth to set in order to realize reaching the engine drive force characteristic of maximum speed Vmax goes; The rotation speed change of the speed of a motor vehicle driving engine during the correspondence cruising is bigger, can not select the high engine speed region cruising of fuel consumption rate, so fuel consumption rate descends.
Especially; In engine drive in the motor vehicle driven by mixed power that is mounted with big free air capacity driving engine and the electric motor driven combination; Owing to be big free air capacity driving engine; So the residue propulsive effort is bigger, has the obvious problem that descends of the first bang path IFO intermediate fuel oil rate of consumption at the driving device of the setting that comprises described low coefficient ratio of number of teeth.In addition; Even with the situation of this big free air capacity driving engine combination under; On big free air capacity multicylinderengine, output characteristic changeable mechanisms such as cylinder deactivation are made up; To realize the raising of fuel consumption rate, can not give full play of under the setting of aforesaid low coefficient ratio of number of teeth the advantage of the changeable mechanism of the output characteristic that the cylinder that carries out in order to improve fuel consumption rate is variable.
In addition, in the special permission document 1, do not mention the system of selection by the motoring condition of chaufeur control such as relevant shifter bar, therefore, can not deal with not situation according to driver intention.
Summary of the invention
The present invention is in view of the above problems and exploitation that its objective is provides a kind of motor vehicle driven by mixed power, can further improve the vehicle fuel consumption rate, and can carry out the selection according to the motoring condition of the intention of chaufeur.
The present invention provides a kind of motor vehicle driven by mixed power; It possesses: engine drive power is passed to first bang path of drive wheel and motor force is passed to second bang path of said drive wheel, and select one of which or the two and with and go, wherein; The reduction ratio that first reduction ratio of said first bang path is set at than only utilizes the maximum speed that said engine drive power can reach is little; And the propulsive effort property settings of said electrical motor does, near the maximum speed of motor vehicle driven by mixed power; The peak output characteristic curve of electrical motor is higher than the motion-resistance-force characteristics curve, only utilizes the driving of electrical motor just can realize maximum speed.
Description of drawings
Fig. 1 is the motor vehicle driven by mixed power single-piece generalized schematic of first embodiment of the invention;
Fig. 2 is the propulsive effort characteristic map of the motor vehicle driven by mixed power of first embodiment;
Fig. 3 is the motor vehicle driven by mixed power single-piece generalized schematic of second embodiment of the invention;
Fig. 4 is used to carry out switching that the engine drive power of the motor vehicle driven by mixed power of second embodiment is transmitted to drive wheel through first bang path and the power-transfer clutch of speed change, the assembly drawing of clutch segment brakeage explanation;
Fig. 5 is the scheme drawing of control of the make and break device of explanation motor vehicle driven by mixed power of the present invention;
Fig. 6 is the diagram of circuit of the control of the make and break device when being used to the operation of carrying out driver requested large driving force is described;
Fig. 7 is the scheme drawing of main portion of the variation of explanation present embodiment.
The specific embodiment
First embodiment
Below, with reference to Fig. 1, Fig. 2 and Fig. 5 the motor vehicle driven by mixed power of the first embodiment of the present invention is described.
Fig. 1 is the motor vehicle driven by mixed power single-piece generalized schematic of the embodiment of the invention, and expression is through the electrical motor of fixed gear wheel speed change and the bang path of engine drive power.
Fig. 2 is the propulsive effort characteristic map of the motor vehicle driven by mixed power of present embodiment.In Fig. 2, transverse axis is represented the speed of a motor vehicle, and the longitudinal axis is represented propulsive effort or car resistance.
Fig. 5 is the scheme drawing of control of the make and break device of explanation motor vehicle driven by mixed power of the present invention.
The formation of the motor vehicle driven by mixed power 50A of the embodiment of the invention is; Possess propulsive effort with driving engine 1 and be delivered to drive wheel 6 and make first bang path of vehicle ' and the propulsive effort of electrical motor 8 is delivered to drive wheel 6 and makes second bang path of vehicle ', select these first bang paths and second bang path one or both of and with and go.
As shown in Figure 1, the output shaft 2 of the driving engine 1 that many cylinders for example are made up of 6 cylinders directly links via the electrical generator 4 of flywheel 3 with the double as starter, and, and be used for the power-transfer clutch 5A that propulsive effort with driving engine 1 is delivered to drive wheel 6 and be connected.
Below, first bang path is described.
First bang path comprises: output shaft 2, power-transfer clutch 5A, through power-transfer clutch 5A engages with output shaft 2 or open circuited main gear 11, with main gear 11 ingear output gears 12, with the miniature gears 13 of output gear 12 coaxial drive, and miniature gears 13 ingear main reduction gears 14 and import the diff 7 that drives drive wheel 6 by main reduction gear 14.The propulsive effort of driving engine 1 passes to drive wheel 6 through said first bang path.
Power-transfer clutch 5A is an oil clutch, leaves, closes through actuator 33A.And the power of driving engine 1 passes to drive wheel 6 through the connection (engagement state) of power-transfer clutch 5A, cuts off the transmission to drive wheel 6 through the separation (off-state) of power-transfer clutch 5A.In addition, when the needs large driving force, power-transfer clutch 5A separates, and as hereinafter described, the propulsive effort of electrical motor 8 is delivered to drive wheel 6.
Also have, this first bang path has definite fixing first reduction ratio of the present invention with the product of the ratio of number of teeth of the ratio of number of teeth of main gear 11 and output gear 12 and miniature gears 13 and main reduction gear 14, does not have the driving device of variable ratio of number of teeth.Main gear 11, output gear 12, miniature gears 13, main reduction gear 14 constitute the reductor 9A of the drive wheel 6 that drives for driving engine 1.
In addition, as shown in Figure 5, when requiring the L shelves of large driving force, motor vehicle driven by mixed power drives actuator 33A with ECU23A through electric signal and makes 51 work of oil pressure pressure regulating valve by driver's operation shifter bar 52.This oil pressure pressure regulating valve 51 control oil pressure and carry out power-transfer clutch 5A from, close control, make power-transfer clutch 5A become the open state of separation, the transmission of the propulsive effort of combustion cutoff 1 makes and passes to drive wheel 6 from the propulsive effort of electrical motor 8.In addition, oil pump 53 supplies to power-transfer clutch 5A through the running of motor vehicle driven by mixed power with the electrical motor M54 of the electric signal control of ECU23A with power fluid.
And motor vehicle driven by mixed power is used ECU23A, when for example shifter bar 52 has been operated the L shelves, drives actuator 33A and makes 51 work of oil pressure pressure regulating valve, thereby power-transfer clutch 5A is separated.
In addition, hand valve 56 mechanical connections that possess in shifter bar 52 usefulness metal wools 55 and the oil hydraulic circuit between power-transfer clutch 5A and oil pump 53.At this moment, when shifter bar 52 moves to the L shelves, also can be not according to the instruction of motor vehicle driven by mixed power with ECU23A, but the interlocking mechanism through metal wool 55 close hand valve 56 so that power-transfer clutch 5A separates.
At this, first reduction ratio of retarder 9A is set as follows.Propulsive effort characteristic during the roughly peak output of the driving engine 1 when motor vehicle driven by mixed power 50A of the present invention normally drives a vehicle is shown in the characteristic curve a of Fig. 2; According to respect to the engine speed of the speed of a motor vehicle of said first reduction ratio and the relation of moment of torsion; Near maximum speed Vmax; Propulsive effort is lower than car resistance characteristic curve b, and the big or small level of propulsive effort can only accelerate to speed V 4.That is, the ratio of number of teeth predetermined fixed of reductor 9A be the motor vehicle driven by mixed power 50A that reached than carried driving engine 1 only utilize gear that the propulsive effort of driving engine 1 can reach maximum speed Vmax than the time the gear ratio of the little propulsive effort of propulsive effort.The motor vehicle driven by mixed power 50A of present embodiment only utilizes the propulsive effort of driving engine 1 can not realize the structure of maximum speed Vmax.
In addition, the car resistance characteristic curve b of Fig. 2 is the resistance addition curve afterwards that the corresponding speed of a motor vehicle such as rotational resistance and air resistance is increased.
In addition, so-called " during cruising " is meant that being in the speed of a motor vehicle rises from speed V 1 (second speed of a motor vehicle) to the situation that is lower than the middle and high vehicle speed range (second vehicle speed range) the V4 (first speed of a motor vehicle).
In addition, as shown in Figure 1, through changer 21 from electrical generator 4 or battery 20 supply capabilities and driven electrical motor 8, the input gear 8b and main gear 11 engagements that directly link with its motor reel 8a.
Below, second bang path is described.
Second bang path comprises: input gear 8b, main gear 11, with main gear 11 ingear output gears 12, drive the diff 7 of drive wheel 6 by the miniature gears 13 of coaxial drive, with miniature gears 13 ingear main reduction gears 14 and from main reduction gear 14 inputs with output gear 12.The propulsive effort of electrical motor 8 passes to drive wheel 6 through said second bang path.
In addition; The fixing reduction ratio that the product of the ratio of number of teeth of ratio of number of teeth, main gear 11 and output gear 12 that this its ratio of number of teeth of second bang path is input gear 8b and main gear 11 and the ratio of number of teeth of miniature gears 13 and main reduction gear 14 is confirmed does not have the driving device of variable ratio of number of teeth.
Peak output characteristic curve c among Fig. 2 representes the peak output characteristic of electrical motor 8.Peak output characteristic curve c is a maximum driving force to the low speed of a motor vehicle of regulation when motor vehicle driven by mixed power 50A starts to walk, and thereafter, along with the speed of a motor vehicle rises, that is, along with the rotating speed of electrical motor 8 rises, propulsive effort sharply reduces.And the propulsive effort property settings of electrical motor 8 is that near the maximum speed Vmax of motor vehicle driven by mixed power 50A, the peak output characteristic of electrical motor 8 is higher than motion-resistance-force characteristics curve b, only utilizes electrical motor 8 to drive and just can realize maximum speed Vmax.
As shown in Figure 1, in order to control the operative condition of motor vehicle driven by mixed power 50A, be provided with motor vehicle driven by mixed power with ECU (ECU:Electric Control Unit) 23A.From the ignition lock signal of ignition lock 35, from the shift signal of being located at the MLP sensor 36 on the not shown shifter bar, from the Das Gaspedal depression amount signal of being located at the accelerator pedal position sensor 37 on the not shown Das Gaspedal, from the brake pedal depression amount signal of being located at the brake pedal position sensor 38 on the not shown brake pedal, from the GES of being located at the car speed sensor 39 on the wheel, the input motor vehicle driven by mixed power is with among the ECU23A.
In addition, battery 20 is provided with the various sensors of not shown detection output voltage, outgoing current, battery temperature, and its various sensor signals are input to motor vehicle driven by mixed power with among the ECU23A.
Motor vehicle driven by mixed power is with ECU23A control actuator 33A, and wherein, actuator 33A is reflected as Das Gaspedal depression amount and brake pedal depression amount according to GES, power-transfer clutch 5A is in engages or released state.
In addition, motor vehicle driven by mixed power through the electrical generator 4 of changer 21 control double as starters and the electrical motor 8 that can generate electricity, is controlled the running of driving engines 1 with ECU23A through the Engine ECU 25 of control output characteristic changeable mechanism 31 grades.
Motor vehicle driven by mixed power is connected with Engine ECU 25 usefulness communication lines with ECU23A; Except that from the control signal of motor vehicle driven by mixed power with ECU23A, shift position signal, Das Gaspedal depression amount, brake pedal depression amount signal, GES etc. are input in the Engine ECU 25.On the contrary, the rotating speed of Engine ECU 25 detection of engine 1 etc. are input to motor vehicle driven by mixed power with among the ECU23A through communication line.
Constituting of output characteristic changeable mechanism 31 for example comprises: variable control to the ascending amount that does not have graphic valve that is provided with at the cylinder 1a of driving engine 1, open and close timer-operated mechanism; The valve that makes a part of cylinder 1a does not drive and the mechanism that carries out the control (cylinder shuts down) of the variable cylinder of cylinder deactivation; Carry out the time-controlled electronic loop of point of ignition; Carry out the mechanism and the electronic loop of fuel injection control.
The 3 cylinder cylinder deactivations that the characteristic curve d of Fig. 2 representes to utilize the action of output characteristic changeable mechanism 31 that a side of 6 cylinder engines 1 is arranged, the propulsive effort characteristic of the roughly peak output state of the driving engine 1 when having only the cylinder deactivation running of 3 remaining cylinder operations.Only utilize engine drive power, under above-mentioned first reduction ratio, only reach speed V 3 according to the low outputization of this cylinder deactivation operative condition.
(switching controls of bang path)
In above structure, motor vehicle driven by mixed power is as follows with ECU23A, switches first bang path and second bang path goes motor vehicle driven by mixed power 50 according to the speed of a motor vehicle.
When the low vehicle speed range when the starting that comprises from the speed of a motor vehicle shown in Figure 20 to not enough speed V 1 (second speed of a motor vehicle), up-hill journey and during driver's operation shifter bar 52 to L shelves etc.; Control actuator 33A makes power-transfer clutch 5A between output shaft 2 and the main gear 11 of driving engine 1 side and cuts off, and control change device 21 utilizes electrical motor 8 to drive drive wheel 6 through second bang path.At this moment, electrical motor 8 relies on the electric power from battery 20 to be driven.If battery 20 charge conditions after a little while, motor vehicle driven by mixed power is with ECU23A control change device 21 and Engine ECU 25, makes electrical generator 4 as starter performance function and fire an engine 1.And control change device 21 makes by 4 generatings of 1 pair of electrical generator of driving engine, its driven by power electrical motor 8 (series running pattern).In addition, after in the parallel operation pattern stated, driver's operation shifter bar 52 (with reference to Fig. 5) will be from the parallel operation pattern to above-mentioned series running mode converting during to the L shelves.
The peak output characteristic of electrical motor 8 near maximum speed Vmax, has the propulsive effort that is higher than motion-resistance-force characteristics curve b shown in the peak output characteristic curve c of Fig. 2.Therefore, rely on the propulsive effort of electrical motor 8, motor vehicle driven by mixed power 50A can go in above-mentioned low-speed range.
When the middle and high vehicle speed range from speed V 1 to not enough speed V 4 (first speed of a motor vehicle) (second vehicle speed range) cruising; Motor vehicle driven by mixed power is with ECU23A control actuator 33A; Power-transfer clutch 5A is connected with the output shaft 2 of driving engine 1 side; Changer 21 does not make electrical motor 8 drive in principle, and therefore, just the propulsive effort of driving engine 1 is delivered to drive wheel 6 through first bang path.The propulsive effort of the drive wheel 6 of this moment is according to characteristic curve a shown in Figure 2 or characteristic curve b.In addition; During the cylinder deactivation running; Owing to only accelerate to the speed V 3 of the scope of the propulsive effort that is higher than motion-resistance-force characteristics curve b; So Engine ECU 25 is according to the speed of a motor vehicle and shift position signal, Das Gaspedal depression amount control output characteristic changeable mechanism 31, and applies in a flexible way and switch 6 cylinder operations and 3 cylinder operations to reach best fuel consumption rate.
In addition, electrical motor 8 companion rotations this moment (idle running).
During acceleration during going with the middle and high speed of a motor vehicle of the speed of a motor vehicle from V1 to not enough V4; Motor vehicle driven by mixed power drives electrical motor 8 auxiliary engines with ECU23A control change-speed box 21; During opposite the deceleration, motor vehicle driven by mixed power makes electrical motor 8 regenerative electric powers with ECU23A control change-speed box 21.
Secondly; The max speed scope (first vehicle speed range) of the speed of a motor vehicle from high speed V 4 (first speed of a motor vehicle) to maximum speed Vmax, motor vehicle driven by mixed power becomes the output shaft 2 bonded assembly states that make power-transfer clutch 5A and driving engine 1 side with ECU23A control actuator 33A; The propulsive effort of driving engine 1 passes to drive wheel 6 via first bang path; Simultaneously, control change device 21 makes electrical motor 8 rotations, and its propulsive effort passes to drive wheel 6 via second bang path.That is, become parallel operation pattern by the driving of electrical motor 8 assistive drive driving engines 1.At this moment, motor vehicle driven by mixed power with ECU23A after a little while at battery 20 charge conditions, control change device 21 makes electrical generator 4 generating, utilizes its driven by power electrical motor 8.
Below, the treatment scheme when driver requested large driving force is described.Fig. 6 is the diagram of circuit that is used to explain the control of the make and break device when chaufeur carries out the operation of requirement large driving force.
Motor vehicle driven by mixed power with ECU (in the explanation of this diagram of circuit, be called for short " ECU ") 23A judge gear signal whether be " L " (S1), (No of S1) then do not shift to S2 and handles when not being " L "; (Yes of S1) then moves on to S8 and handles when being " L ".And in S2, whether ECU23A judge and to require torque rating littler than Tref, and (Yes of S2) then moves on to S3 and handle when satisfying this condition, and (No of S2) then moves on to S6 and handle when not satisfying this condition.At this, Tref representes directly to break off the highest moment of torsion that obtains.In addition, requiring moment of torsion is the moment of torsion that is used to obtain the propulsive effort of needs.
In S3,, judge whether the value of the speed of a motor vehicle is bigger than Vref because the value that requires moment of torsion than Tref little (Yes of S2), therefore, is followed in S3.At this, the value of the speed of a motor vehicle can be envisioned for and shows that chaufeur further requires situation about quickening when Tref is following.Because vehicle speed value is than Vref big (Yes of S3), so ECU23A makes magnet coil (actuator 33A) work (S4), make direct coupled power-transfer clutch 5A separate (S5), return S1.
In addition, in S6, owing to require torque rating than Tref big (No of S2), perhaps, vehicle speed value so ECU23A does not work (S6) magnet coil, and makes direct coupled power-transfer clutch 5A engage (S7) than Vref little (No of S3), returns S1.On the other hand, because gear signal is " L " (Yes of S1), ECU23A does not allow magnet coil work (S8), makes direct coupled power-transfer clutch 5A engage (S9), and then S 1 is returned in the output (S10) of restriction oil pump (EOP (electric oil pump)) 53.
According to present embodiment; Motor vehicle driven by mixed power 50A; In low vehicle speed range from the speed of a motor vehicle 0 to not enough authorized speed V1; Utilize the high electrical motor of propulsive effort 8 can realize the propulsive effort of the peak output characteristic curve c of Fig. 2, in this low vehicle speed range, utilize the large driving force of electrical motor 8 easily to go.Thereby, even also can use under the travel situations of the bigger propulsive effort of needs such as going in the ramp.And; The speed of a motor vehicle rises and from middle and high vehicle speed range (second speed of a motor vehicle) cruising of speed V 1 (second speed of a motor vehicle) to not enough V4 (first speed of a motor vehicle) time; Shown in characteristic curve a or characteristic curve d; The propulsive effort characteristic of driving engine 1 is higher than motion-resistance-force characteristics curve b, therefore, only utilizes driving engine 1 just can go.
As shown in Figure 2; The characteristic curve a of present embodiment, the characteristic curve f of the propulsive effort of the driving engine 1 when its driving force ratio is set the reduction ratio of first bang path is little, makes driving engine with lower low rotation high loaded process with respect to identical resistance to motion; The feasible existing engine drive power of only putting down in writing with characteristic document 1; Just can realize the maximum speed Vmax of motor vehicle driven by mixed power 50A, therefore, the existing motor vehicle driven by mixed power of fuel consumption rate ratio characteristic document 1 record improves.Moreover, do not need propulsive effort and under situation such as flatly go, though the drive performance when turning round by the cylinder deactivation shown in the characteristic curve d also can go, can be with higher fuel consumption rate cruising.
Especially in the engine drive and electric motor driven combination of the motor vehicle driven by mixed power 50A that big free air capacity driving engine is installed as driving engine 1; Because during cruising be big free air capacity driving engine; So the residue propulsive effort becomes big; The ratio of number of teeth of reductor 9A becomes the setting than the ratio of number of teeth of the higher coefficient of said existing motor vehicle driven by mixed power, and therefore, fuel consumption rate is compared remarkable improvement with existing.In addition; When making up with the sort of large-duty engine; Combination comprises the changeable mechanism 31 of the output characteristic of cylinder deactivation function etc. on the multiple cylinder engine of big free air capacity; Reduce driving engine output and become the good engine rotary speed of combustion efficiency, can realize the raising of fuel consumption rate efficient thus.
And; The maximum speed scope (first vehicle speed range) of the speed of a motor vehicle from V4 (first speed of a motor vehicle) to maximum speed Vmax; Can not realize the desirable speed of a motor vehicle because only utilize the propulsive effort of driving engine 1; So, utilize the propulsive effort auxiliary engine propulsive effort of electrical motor 8 by second bang path, can realize the desirable speed of a motor vehicle thus.
In addition; When motor vehicle driven by mixed power 50A arrives the L shelves at operation shifter bar 52, make power-transfer clutch 5A separation and cut off transmission, be used to drive force drive wheel 6 from electrical motor 8 from the propulsive effort of driving engine 1; Therefore, the vehicle large driving force that can utilize electrical motor 8 to provide goes.So, can reflect and will go to the L shelves with the intention that large driving force goes through driver's operation.
Thereby, according to present embodiment, when motor vehicle driven by mixed power 50A selects propulsive effort to require (torque demand) big state at chaufeur,, can realize realizing series running (electric operation) state of big propulsive effort usually through cut-off clutch 5A.
In addition; Because of occurring in, the problem of valve combines the countermeasure of side (losing oil pressure) when blocking fault as the power-transfer clutch 5A that relies on oil pressure actuated; Usually, under the direct connection state, can only carry out going of little propulsive effort, but according to present embodiment; Reduce clutch pressure through shifter bar 52 is moved to the L shelves, just can carry out the subsequent use action of going under the series running (electric operation).
Second embodiment
Below, with reference to Fig. 3 and Fig. 4 (suitably with reference to Fig. 2) motor vehicle driven by mixed power of the second embodiment of the present invention is described.
Fig. 3 is the motor vehicle driven by mixed power single-piece generalized schematic of the embodiment of the invention, the bang path of expression electrical motor and engine drive power.
The motor vehicle driven by mixed power 50B of present embodiment possesses: the propulsive effort of driving engine 1 is delivered to drive wheel 6 makes first bang path of vehicle ' and the propulsive effort of electrical motor 8 is delivered to second bang path that drive wheel 6 makes vehicle ', select these first bang paths and second bang path one or both of and with and go.In hybrid vehicle two 50B of second embodiment; With the motor vehicle driven by mixed power 50A difference among first embodiment be; Substitute the direct connection power-transfer clutch 5A of first embodiment, the planetary wheel (variable gear) 10 as the variable-speed motor of the dual-ratio reduction ratio of changeable direct connection, speedup has been installed.This planetary wheel 10 is provided with from the actuator 33B of the reduction ratio of first bang path separation output shaft 2 or switching controls planetary wheel 10 and power-transfer clutch (make and break device) 5B and the clutch segment drg 5C that is driven by actuator 33B.
Below, the coupled condition of planetary wheel 10 is described in further detail.Planetary gear carrier 17 direct connections of output shaft 2 and the miniature gears 16 that keeps planetary wheel 10.Axle with miniature gears 16 ingear sun gears 15 can be connected, separate through power-transfer clutch 5B with output shaft 2, simultaneously, and the switching that can be rotated, stop through clutch segment drg 5C.In addition, towards with the axle of the inboard ring gear 18 of miniature gears 16 ingears, with motor reel 8a direct connection, on the main body that keeps ring gear 18, be provided with main gear 11, main gear 11 and output gear 12 engagements towards foreign side.
As shown in Figure 3, the output shaft 2 of the driving engine of being made up of 6 cylinders 1 is through electrical generator 4 direct connections of flywheel 3 with the double as starter, and, and be used for the power-transfer clutch 5B that propulsive effort with driving engine 1 is delivered to drive wheel 6 and be connected.
Below, first bang path is described.
First bang path comprises: output shaft 2, power-transfer clutch 5B, be located at through power-transfer clutch 5B be connected with output shaft 2 or the planetary wheel 10 that cuts off on main gear 11, with main gear 11 ingear output gears 12, with the miniature gears 13 of output gear 12 coaxial drive, with miniature gears 13 ingear main reduction gears 14 and by main reduction gear 14 inputs and drive the diff 7 of drive wheel 6.The propulsive effort of driving engine 1 passes to drive wheel 6 through said first bang path.
In addition, planetary wheel 10, main gear 11, output gear 12, miniature gears 13, main reduction gear 14 constitute the retarder 9B that drives drive wheel 6 with respect to driving engine 1.
The reduction ratio of this first bang path is described below, and can switch to the dual-ratio reduction ratio according to the state of power-transfer clutch 5B, clutch segment drg 5C action.When power-transfer clutch 5B engaged (ON) and clutch segment drg 5C separation (OFF), the axle of the sun gear 15 of planetary wheel 10 and the axle of planetary gear carrier 17 were fixed by power-transfer clutch 5B.And, because sun gear 15 and the rotation of planetary gear carrier 17 one, so the reduction ratio of planetary wheel 10 is 1.In the present embodiment, by the ratio of number of teeth of main gear 11 and output gear 12, and the reduction ratio confirmed of the product of the ratio of number of teeth of miniature gears 13 and main reduction gear 14 also become first reduction ratio with the first embodiment equal values.That is,, use the consideration method identical to set with first embodiment based on the drive performance of the driving engine 1 of first reduction ratio of reductor 9B.
Then; When power-transfer clutch 5B separates (OFF) and clutch segment drg 5C joint (ON); The state that the rotation of the axle of the sun gear 15 of planetary wheel 10 is being stopped by clutch segment drg 5C braking; Along with the rotation of the sun gear 15 that centers on planetary gear carrier 17, miniature gears 16 and planetary gear carrier 17 equidirectional rotations, thus make ring gear 18 in above-mentioned same hand of rotation speedup.At this moment, the reduction ratio of first bang path ratio of number of teeth that becomes ratio of number of teeth and the miniature gears 13 and the main reduction gear 14 of reduction ratio, main gear 11 and output gear 12 between above-mentioned speedup state lower planetary gear frame 17 and the ring gear 18 multiply each other definite, than first reduction ratio little second reduction ratio.
Second slows down less than first reduction ratio; Drive performance during based on 6 cylinder operations of the drive performance of the driving engine 1 of second reduction ratio characteristic curve e as shown in Figure 2; Driving engine 1 is under the peak output state of cylinder deactivation running; The max speed V3 than realizing based on the state of first reduction ratio is low, can only accelerate to the max speed V2.That is, second reduction ratio is set at, the engine drive power during the max speed V2 of 6 cylinder operations during second reduction ratio, the engine drive power during the max speed V3 of the cylinder deactivation running when being lower than first reduction ratio.
In addition, through changer 21 by electrical generator 4 or battery 20 supply capabilities and driven electrical motor 8, its motor reel 8a and main gear 11 direct connections.
Below, second bang path is described.
Second bang path comprises: main gear 11, with main gear 11 ingear output gears 12, with the miniature gears 13 of output gear 12 coaxial drive, with miniature gears 13 ingear main reduction gears 14 and by main reduction gear 14 inputs and drive the diff 7 of drive wheel 6.Through said second bang path, the propulsive effort of electrical motor 8 passes to drive wheel 6.
Have, this second bang path is the fixing reduction ratio that the product of ratio of number of teeth of ratio of number of teeth and the miniature gears 13 and the main reduction gear 14 of main gear 11 and output gear 12 is confirmed again, does not have the driving device of variable ratio of number of teeth.
In order to control the operative condition of this motor vehicle driven by mixed power 50B, be provided with motor vehicle driven by mixed power and use ECU23B.Motor vehicle driven by mixed power uses ECU23B to control actuator 33B based on GES reaction as Das Gaspedal depression amount and brake pedal depression amount, control actuator 33B with power-transfer clutch 5B and clutch segment drg 5C individually be controlled at respectively from, close state.Motor vehicle driven by mixed power removes with ECU23B that above-mentioned some is identical with external structure, and is the same with ECU23B with the motor vehicle driven by mixed power of first embodiment, connects battery 20, changer 21 and Engine ECU 25 and carries out same handshaking and control with order wire.
In addition, motor vehicle driven by mixed power is the same with ECU23A with the motor vehicle driven by mixed power of first embodiment with ECU23B, carry out when requiring the instruction of large driving force by chaufeur input power-transfer clutch 5B from, close.In addition, action regularly can be used the processing of the flowchart text of Fig. 6, its explanation of Therefore, omited equally.
In addition, on driving engine 1, be provided with changeable mechanism 31 with the identical output characteristic of first embodiment.
The structure identical with first embodiment paid prosign and omitted the explanation of repetition.
(switching of bang path and variable speed control)
In above structure, motor vehicle driven by mixed power is described below with ECU23B, switches first bang path and second bang path according to the speed of a motor vehicle, and in addition, the reduction ratio that switches first bang path goes motor vehicle driven by mixed power 50B.
Fig. 4 is the assembly drawing of the operating state of power-transfer clutch 5B and clutch segment drg 5C in the motoring condition of motor vehicle driven by mixed power 50B.
Low vehicle speed range when comprising the speed of a motor vehicle 0 from propulsive effort characteristic map shown in Figure 2 to the starting of not enough speed V 1 (second speed of a motor vehicle), when climbing is gone, and by the driver's operation shifter bar during to the L shelves etc. in; Motor vehicle driven by mixed power passes through actuator 33B with ECU23B; As shown in Figure 4; Make power-transfer clutch 5B and clutch segment drg 5C separate (OFF), become the pattern of series running (direct motor drive).Can know by Fig. 3, power-transfer clutch 5B, when clutch segment drg 5C closes (OFF), no matter planetary gear carrier 17 stops or rotate, the number of teeth difference of ring gear 18 and miniature gears 16 absorbs through sun gear 15 idle running, so output shaft 2 and ring gear 18 become released state.Like this, driving engine 1 is separated from first bang path, motor vehicle driven by mixed power is driving motor 8 with ECU23B control change-speed box 21, and drives electrical generator 4 generatings as required, through second bang path propulsive effort of electrical motor 8 is passed to drive wheel 6.Like this, when the low starting of the speed of a motor vehicle, when the low speed of a motor vehicle is gone, electrical motor carries out the high drive running, thereby motor vehicle driven by mixed power 50B is gone.
Also have, after in the parallel operation pattern stated, driver's operation shifter bar 52 (with reference to Fig. 5) is during to the L shelves, from the parallel operation pattern to above-mentioned series running mode conversion.
Then; During cruising state more than the speed of a motor vehicle reaches speed V 1 (second speed of a motor vehicle); Control change device 21 stops the driving of electrical motor 8, and motor vehicle driven by mixed power makes vehicle go with the state of the second good reduction ratio of the fuel consumption rate of driving engine 1 direct coupled 6 cylinder operations shown in the ratio characteristic curve a with ECU23B.That is, as shown in Figure 4, through actuator 33B make power-transfer clutch 5B become separation (OFF), clutch segment drg 5C becomes joint (ON), makes being rotated in the planetary wheel 10 speedup and being delivered to output gear 12 (engine drive in speedup stage) of output shaft 2.The peak output drive performance of the driving engine 1 of this moment is shown in the characteristic curve e of Fig. 2, need not be with the floorboarded propulsive effort that can obtain needs.But; This planetary wheel 10 is under the state in speedup stage; And the reduction ratio at reductor 9B becomes under the state of second reduction ratio; As shown in Figure 2, only reach the highest speed V 2, the propulsive effort during maximum speed V3 during the peak output of the driving engine 1 of the cylinder deactivation operative condition of the driving force ratio of speed V 2 under the direct connection state of driving engine 1 is little.
In addition, this power-transfer clutch 5B, clutch segment drg 5C as during above-mentioned state, driving engine output has when more than needed, as required, Engine ECU 25 makes driving engine 1 carry out cylinder deactivation and turns round.
In addition; Near speed V shown in Figure 22; When speed of a motor vehicle increase is above above it; Motor vehicle driven by mixed power makes power-transfer clutch 5B engage (ON) with ECU23B through actuator 33B, and makes clutch segment drg 5C close (OFF), thereby makes sun gear 15 and planetary gear carrier 17 one rotations (driving of driving engine direct connection).And; Propulsive effort such as flatly go can be smaller, that the Das Gaspedal depression amount hour is judged as the moment of torsion that needs is little; Engine ECU 25 is utilized the driving engine 1 low output running of cylinder deactivation running; And the low output running of the driving engine that utilizes one group of cylinder deactivation to turn round, the rotation of output shaft 2 be not through planetary wheel 10 decelerations and under the direct connection state, be delivered to output gear 12.
Moreover, the same in the vehicle speed range acceleration of middle and high speed, when slowing down with first embodiment, make electrical motor 8 assistive drive respectively or make it regenerative electric power.
And, from speed V more than 4 in the scope of maximum speed Vmax, motor vehicle driven by mixed power is used ECU23B, carries out the control identical with first embodiment.That is, become the pattern of the parallel operation that drives by electrical motor 8 auxiliary engines.
As above state bright; Motor vehicle driven by mixed power 50B according to second embodiment; In low vehicle speed range from the speed of a motor vehicle 0 to not enough speed V 1; When the propulsive effort that needs is big, power-transfer clutch 5B and clutch segment drg 5C (OFF) is separated, thereby only utilize electrical motor 8 to carry out the driving (series running) of drive wheel 6.
The speed V 1 (second speed of a motor vehicle) that never comprises maximum speed Vmax is in the scope (second vehicle speed range) of the middle and high speed of a motor vehicle of not enough speed V 4 (first speed of a motor vehicle); In principle under the cruising state; Only utilize driving engine 1 to carry out the driving of drive wheel 6, accept the auxiliary of electrical motor 8 when quickening as required.In the scope (first vehicle speed range) of the maximum speed more than the speed V that comprises maximum speed Vmax 4 (first speed of a motor vehicle), utilize the driving of driving engine 1 and the driving both sides of electrical motor 8 to carry out the driving (parallel operation pattern) of drive wheel 6.
Like this, the scope of the middle and high speed of a motor vehicle that does not comprise maximum speed Vmax is set at utilizes driving engine 1 cruising, and with speed V 4 (first speed of a motor vehicle) corresponding setting first reduction ratio lower than maximum speed Vmax.Thereby; As shown in Figure 2, the characteristic curve a of present embodiment is identical with first embodiment; The characteristic curve f propulsive effort of the propulsive effort of the electrical generator 1 when its driving force ratio is set the reduction ratio of first bang path is little; Make the propulsive effort of the available engine 1 only utilize patent documentation 1 record, can realize the maximum speed Vmax of motor vehicle driven by mixed power 50B, driving engine is turned round under lower low rotation high load capacity with respect to identical car resistance; Therefore, fuel consumption rate improves than existing motor vehicle driven by mixed power.Moreover under the little also passable situation such as flatly go of propulsive effort, the drive performance when turning round according to the cylinder deactivation shown in the characteristic curve d also can be gone, and promptly can realize the cruising that fuel consumption rate is better.
Particularly; In the combination of big free air capacity driving engine as the driving of the engine drive of the motor vehicle driven by mixed power 50B of driving engine 1 and electrical motor is installed; Because during cruising is big free air capacity driving engine; So the residue propulsive effort becomes big, first reduction ratio (ratio of number of teeth) of reductor 9B becomes the setting than the ratio of number of teeth of the higher coefficient of existing motor vehicle driven by mixed power, and the existing vehicle of fuel consumption rate efficiency ratio significantly improves.In addition, with the combination of this large-duty engine the time, assembling comprises the changeable mechanism 31 of the output characteristic with cylinder deactivation function etc. on the multiple cylinder engine of big free air capacity, just can realize the raising of fuel consumption rate.
Second reduction ratio is set at than the little reduction ratio of above-mentioned first reduction ratio, thus the little speed V 2 of attainable speed V 3 when becoming the peak output of above-mentioned first reduction ratio than through the low outputization of above-mentioned output characteristic changeable mechanism 31 time.
That is, the propulsive effort during speed V 2 can become the second reduction ratio speed change of littler propulsive effort, under low-tach cruising state, can realize the rotative speed of the driving engine that fuel consumption rate efficient is good thus.
In addition, identical with the situation of first embodiment, when operation shifter bar 52 arrives the L shelves; Power-transfer clutch 5B is closed and cut off transmission from the propulsive effort of driving engine 1; Be used to drive force drive wheel 6, therefore, can utilize electrical motor 8 to go with big propulsive effort from electrical motor 8.For this reason, the intention that can go with the large driving force that reflection utilizes chaufeur to move to the L shelves and going.
In the present embodiment; In the scope of the maximum speed Vmax of speed V more than 4; As stated, though the parallel operation of using electrical motor 8 auxiliary engines to drive also can be first bang path of combustion cutoff 1; Driving engine 1 drives electrical generator 4 and makes it generating, utilizes the series running of its driven by power electrical motor 8.
In addition, in the present embodiment, make motor reel 8a and main gear 11 direct connections, the same with first embodiment, also can its propulsive effort be delivered to main gear 11 via the input gear 8b that is located on the motor reel 8a.
In first embodiment and second embodiment, maximum speed scope (first vehicle speed range) is set at speed V more than 4, but is not limited to speed V more than 4.Also can the upper limit of middle and high vehicle speed range (second vehicle speed range) be set at the good and lower vehicle speed value of combustion efficiency up to driving engine 1, further reduce the vehicle speed value that switches by electrical motor 8 assistive drive or series running than speed V 4.
The variation of first embodiment and second embodiment
In first embodiment and second embodiment, constitute: the motor force of electrical motor 8 is delivered to main gear 11 through the input gear 8b that is located on the motor reel 8a, and perhaps motor reel 8a and main gear 11 directly link and transmit.And the driving that is produced by electrical motor 8 covers vehicle speed range and the vehicle speed range from speed V 4 to maximum speed Vmax from the speed of a motor vehicle 0 to not enough speed V 1.
But in the vehicle speed range from speed V 4 to maximum speed Vmax, the rotative speed of electrical motor 8 might surpass 10,000 rpm.It is easy that control change device 21 makes electrical motor 8 more speeds rotations, but with respect to the physical construction of the rotor of electrical motor 8, bearing etc., design condition will be stricter, might weight increase for the intensity that improves electrical motor 8.
Therefore, as the distortion of first and second embodiment, the rotating speed that makes motor reel 8a can " direct connection ", " speedup " through the twin-stage variable-speed motor, and the gear of output shaft that also can be through above-mentioned twin-stage variable-speed motor is delivered to main gear 11 with rotation.And; Above-mentioned variable-speed motor can be selected the speed change of above-mentioned twin-stage variable-speed motor through motor vehicle driven by mixed power with ECU23B with ECU23A or motor vehicle driven by mixed power; " directly linking " in the scope of realization from the speed of a motor vehicle 0 to not enough speed V 1, " speedup " from speed V 4 to maximum speed Vmax; Thus, can reduce the rotating speed of the electrical motor 8 in the vehicle speed range from speed V 4 to maximum speed Vmax and use.
In addition, Fig. 7 is the scheme drawing of main portion of another variation of explanation first embodiment and second embodiment.In this variation, replace power-transfer clutch 5A, 5B and possess the claw clutch 5C of direct binding, and possess the electrical actuator 33C that drives the claw clutch 5C that this mechanical type directly links.The claw clutch 5C that this mechanical type directly links leaves, closes through electrical actuator 33C control.
Claims (11)
1. motor vehicle driven by mixed power, it possesses: engine drive power is passed to first bang path of drive wheel and motor force is passed to second bang path of said drive wheel, and select one of which or the two and with and go, it is characterized in that,
It is little that first reduction ratio of said first bang path is set at the reduction ratio that only utilizes said engine drive power can reach maximum speed than vehicle,
And the propulsive effort property settings of said electrical motor is that near the maximum speed of motor vehicle driven by mixed power, the peak output characteristic curve of electrical motor is higher than the motion-resistance-force characteristics curve, only utilizes the driving of electrical motor just can realize maximum speed.
2. motor vehicle driven by mixed power as claimed in claim 1; It is characterized in that, when vehicle reaches said maximum speed, only said motor force is passed to said drive wheel through said second bang path; Perhaps; Through said second bang path said motor force is passed to said drive wheel, simultaneously, said engine drive power is passed to said drive wheel through said first bang path.
3. according to claim 1 or claim 2 motor vehicle driven by mixed power is characterized in that said driving engine has the variable output characteristic changeable mechanism of the output characteristic of making,
In said first bang path; Has the variable gear that to set second reduction ratio; Wherein, Said second reduction ratio is than the little reduction ratio of said first reduction ratio, and this second reduction ratio forms the little propulsive effort of propulsive effort than by the low outputization of said output characteristic changeable mechanism the time, can reach peak output based on the said driving engine of said first reduction ratio when the said low output state time.
4. motor vehicle driven by mixed power as claimed in claim 3 is characterized in that, said output characteristic changeable mechanism makes the cylinder deactivation running of a part of cylinder deactivation in the running of said driving engine.
5. motor vehicle driven by mixed power as claimed in claim 3 is characterized in that, said output characteristic changeable mechanism carries out the open and close controlling of valve, the fixed-time control of point of ignition and at least a control in the fuel injection control.
6. motor vehicle driven by mixed power as claimed in claim 1; It is characterized in that; Said first bang path and said second bang path possess the common output gear that at least one side's in said engine drive power and the said motor force propulsive effort is passed to said drive wheel
More than comprising first speed of a motor vehicle that never comprises the vehicle halted state, in first vehicle speed range of the maximum speed of only utilizing said engine drive power to reach, through said second bang path said motor force is passed to said drive wheel at least,
In second vehicle speed range; When cruising; Through said first bang path said engine drive power is passed to said drive wheel, wherein, said second vehicle speed range is meant from second speed of a motor vehicle lower than the speed of a motor vehicle of said first speed of a motor vehicle and plays the scope that is lower than said first speed of a motor vehicle.
7. motor vehicle driven by mixed power as claimed in claim 1 is characterized in that, also possesses the make and break device of switching said first bang path and said second bang path,
When said make and break device requires the instruction of the propulsive effort bigger than specified value in input, become the open state that keeps connecting said second bang path, cuts off said first bang path, vehicle only utilizes the propulsive effort of said second bang path to go.
8. motor vehicle driven by mixed power as claimed in claim 7; It is characterized in that also possessing to said make and break device and supply with the oil pump of oil pressure and adjustment drives this oil pressure pressure regulating valve by the oil pressure pressure regulating valve of the oil pressure of the oil hydraulic circuit of this oil pump supply with through electric signal actuator.
9. motor vehicle driven by mixed power as claimed in claim 8 is characterized in that, when the open state of said make and break device, limits the propulsive effort of said actuator, limits the driving of said oil pump.
10. motor vehicle driven by mixed power as claimed in claim 9 is characterized in that said make and break device possesses hand valve, and this hand valve mechanically is connected with the shifter bar of driver's operation, supplies with the oil pressure from said oil pump.
11. motor vehicle driven by mixed power as claimed in claim 7 is characterized in that, also possesses the electrical actuator that drives said make and break device through electric signal.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006184565A JP4217253B2 (en) | 2006-07-04 | 2006-07-04 | Hybrid vehicle |
| JP2006-184475 | 2006-07-04 | ||
| JP2006-184565 | 2006-07-04 | ||
| JP2006184565 | 2006-07-04 | ||
| JP2006184475A JP4217252B2 (en) | 2006-07-04 | 2006-07-04 | Hybrid vehicle |
| JP2006184475 | 2006-07-04 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101108586A CN101108586A (en) | 2008-01-23 |
| CN101108586B true CN101108586B (en) | 2012-02-08 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007101278122A Active CN101108586B (en) | 2006-07-04 | 2007-07-03 | Hybrid vehicle |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4217253B2 (en) |
| CN (1) | CN101108586B (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112010002939T5 (en) * | 2009-07-14 | 2012-09-20 | Honda Motor Co., Ltd. | Control for vehicle drive unit |
| DE102009050957B4 (en) * | 2009-10-28 | 2018-07-26 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | mixed hybrid |
| JP5593117B2 (en) * | 2010-04-27 | 2014-09-17 | 本田技研工業株式会社 | Hybrid vehicle drive device |
| JP5201190B2 (en) * | 2010-10-08 | 2013-06-05 | 三菱自動車工業株式会社 | Hybrid vehicle clutch control device |
| US8838313B2 (en) * | 2012-07-06 | 2014-09-16 | GM Global Technology Operations LLC | Extended-range electric vehicle with mechanical output clutch |
| JP6202256B2 (en) * | 2013-06-28 | 2017-09-27 | 三菱自動車工業株式会社 | Vehicle transaxle device |
| JP2015010800A (en) * | 2013-07-01 | 2015-01-19 | 小池酸素工業株式会社 | Exhaust gas treatment device |
| CN104417379A (en) * | 2013-08-27 | 2015-03-18 | 常州昊康新能源科技有限公司 | Main and auxiliary motor coupling and range-extending driving system |
| JP6319611B2 (en) * | 2017-03-29 | 2018-05-09 | 三菱自動車工業株式会社 | Vehicle transaxle device |
| CN109572416B (en) * | 2017-09-28 | 2022-05-13 | 比亚迪股份有限公司 | Power system and vehicle |
| KR102484929B1 (en) * | 2017-12-28 | 2023-01-04 | 현대자동차주식회사 | Method for controlling maximum speed of vehicle driven by motor |
| JP7192408B2 (en) * | 2018-11-06 | 2022-12-20 | トヨタ自動車株式会社 | Hybrid vehicle control device |
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Also Published As
| Publication number | Publication date |
|---|---|
| JP2008012990A (en) | 2008-01-24 |
| CN101108586A (en) | 2008-01-23 |
| JP4217253B2 (en) | 2009-01-28 |
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