CN110271413A - The power device of vehicle - Google Patents
The power device of vehicle Download PDFInfo
- Publication number
- CN110271413A CN110271413A CN201910163042.XA CN201910163042A CN110271413A CN 110271413 A CN110271413 A CN 110271413A CN 201910163042 A CN201910163042 A CN 201910163042A CN 110271413 A CN110271413 A CN 110271413A
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- Prior art keywords
- torque
- vehicle
- power source
- driving wheel
- motor
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
- B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
- B60L15/20—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed
- B60L15/2036—Electric differentials, e.g. for supporting steering 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
- Y02T10/72—Electric energy management in electromobility
Abstract
The power device of vehicle is provided, in the case that failure has occurred in the side in 2 power sources, without stopping vehicle, can also ensure that the stable driving performance of vehicle in turning.The epicyclic gearing of the power device of vehicle of the invention has 5 rotary elements, they meet the revolving speed in nomogram and are arranged in the alignment relationship on single straight line, among these rotary elements, 1st and the 2nd outside rotary element (the 1st and the 2nd sun gear) is coupled with the 1st and the 2nd motor respectively, and the 1st and the 2nd inside rotary element (the 2nd and the 1st gear ring) is coupled with left and right sidesing driving wheel respectively.Moreover, making differential limiting mechanism work when the malfunction of failure has occurred in the side in the 1st and the 2nd motor, being attached between the 1st and the 2nd outside rotary element, and control the braking torque of driving wheel to prevent the sideslip of vehicle.
Description
Technical field
The present invention relates to be able to carry out to each other differential speed rotation left and right sidesing driving wheel transmit power vehicle power device,
In particular to the power transmission of the vehicle of power is controlled using differential limiting mechanism.
Background technique
As the power device of existing vehicle, such as the power device of the vehicle disclosed in known patent document 1.It should
Power device by the power of the 1st and the 2nd motor (motor), via the 1st and the 2nd planetary gear mechanism, transmit to the left by right driving wheel.
1st planetary gear mechanism have the 1st sun gear, the 1st planet carrier and the 1st gear ring, the 2nd planetary gear mechanism have the 2nd sun gear,
2nd planet carrier and the 2nd gear ring.1st planet carrier is coupled with the 1st motor and the 2nd sun gear, the 2nd planet carrier and the 2nd motor and the 1st
Sun gear is coupled.1st gear ring is coupled with left driving wheel, and the 2nd gear ring is coupled with right driving wheel.In addition, in the 1st motor and the 2nd horse
The differential limiting mechanism being made of clutch mechanism is provided between reaching, which is used for by the 1st motor
Mechanicalness is carried out between the second motor to connect to limit the differential of left and right sidesing driving wheel.
In this configuration, the 1st planet carrier (the 1st motor), the 1st gear ring (left driving wheel), the 2nd gear ring (right driving wheel) and
2 planet carriers (the 2nd motor) are that revolving speed is arranged successively in the alignment relationship on straight line on nomogram.Therefore, in the 1st and
In the case that one in 2 motors has occurred and the functional faults such as can not export, the traveling of vehicle can be become difficult, therefore be made
With the dynamic Control of above-mentioned differential limiting mechanism.
Specifically, to the driver notification situation, driver is promoted to stop when being determined as that failure has occurred in a motor
Only vehicle, and stop the output of another normal motor, stop vehicle.Then, differential limiting mechanism is made to work, it will just
The power of normal motor is transmitted to the driving wheel for the motor side that failure has occurred, and thereby, it is possible to keep straight on.
[advanced technical literature]
Patent document 1: International Publication No. 2017/145878
It is using vehicle stopping as item in the case where failure has occurred in a motor but in existing power device
Part drives differential limiting mechanism.Thus, for example in the case where failure has occurred when driving on a highway, from a high speed
In a period of driving status actually stops to vehicle, the dynamic Control of reply malfunction can not be carried out completely, so as to
It is unable to ensure the stable driving performance of vehicle.In the case where the failure of motor especially has occurred in turning, lead sometimes
Cause vehicle idle running or exception it is disabled, the problem is especially significant in this case.
Summary of the invention
The present invention is to complete to solve the above problem, and its purpose is to provide the power devices of following vehicle:
One in 2 power sources in the case where failure has occurred, without stopping vehicle, even if can also ensure that vehicle in turning
Stable driving performance.
In order to achieve the above objectives, the invention of first aspect is the power device 1 of vehicle, to can carry out differential each other
Left and right sidesing driving wheel WL, WR of rotation transmit power, and the power device 1 of the vehicle is characterized in that, comprising: the 1st power source and the 2nd
Power source ((hereinafter, identical in present aspect) the 1st and the 2nd motor MG1, MG2 in embodiment)；And geared system (row
Star gear device PG), there are the multiple rotary elements constituted by 4 or 5, the multiple rotary element is configured to,
Meet the alignment relationship that revolving speed is arranged on single straight line in nomogram arranging in multiple rotary elements of geared system
In line chart be located at two outside the 1st and the 2nd outside rotary element (the 1st and the 2nd sun gear S1, S2) respectively with the 1st and the 2nd power
Source is coupled, and the 1st and the 2nd inside on and position in the inner part adjacent with the 1st and the 2nd outside rotary element is located in nomogram
Rotary element (the 2nd gear ring R2 and the 1st gear ring R1) is coupled with left and right sidesing driving wheel WL, WR respectively, and the power device 1 of the vehicle has
Have: (ECU 2, the step 1) of Fig. 4 require target torque setup unit according to driving wheel required by left and right sidesing driving wheel WL, WR
Torque sets the target torque (target torque TM1, TM2) of the 1st and the 2nd power source；Differential limiting mechanism MC, is used to pass through
The differential of left and right sidesing driving wheel WL, WR is limited to being attached between the 1st and the 2nd outside rotary element；Brake apparatus SD is right
Left and right sidesing driving wheel WL, WR are braked independently of one another；Malfunction judging unit (ECU 2, the step 3) of Fig. 4, to whether
It produces malfunction to be determined, which is the shape that functional fault has occurred in a side in the 1st and the 2nd power source
State；And control unit (ECU 2, the step 12 of Fig. 4,13), when being judged to that malfunction has occurred, by making differential limit
Mechanism MC processed work and to being attached between the 1st and the 2nd outside rotary element, and left and right is applied to brake apparatus SD and is driven
The braking torque of driving wheel WL, WR are controlled, to prevent the sideslip of the vehicle.
According to this structure, the power device of vehicle has the tooth being set between the 1st and the 2nd power source and left and right sidesing driving wheel
Wheel apparatus.There are the geared system the multiple rotations constituted by 4 or 5 that revolving speed meets alignment relationship in nomogram to want
Element.In this multiple rotary element, the 1st and the 2nd outside rotary element in two outsides is located in nomogram respectively with the 1st and the
2 power sources are coupled, the 1st and the 2nd inside rotation on and position in the inner part adjacent with the 1st and the 2nd outside rotary element
Element is coupled with left and right sidesing driving wheel respectively.In addition, requiring torque to set the 1st He according to driving wheel required by left and right sidesing driving wheel
The target torque of 2nd power source.
According to the above structure, the power of the 1st and the 2nd power source based on target torque is respectively inputted to geared system
1st and the 2nd outside rotary element is assigned via the 1st and the 2nd inside rotary element, is transmitted to left and right sidesing driving wheel.As a result,
The driving wheel of left and right is driven, and the torque of driving wheel is controlled as driving wheel requirement torque.
In addition, making differential when the malfunction of functional fault has occurred in the side being determined as in the 1st and the 2nd power source
Limiting mechanism work, is attached between the 1st and the 2nd outside rotary element.There is no the dynamic of the power source of failure as a result,
Power is passed to driving wheel via the outside rotary element for the power source that failure has occurred.Also, it is being judged to having occurred
When above-mentioned malfunction, the sideslip to prevent vehicle is controlled the braking torque that brake apparatus is applied to left and right sidesing driving wheel.
In this way, when failure has occurred in the side in the 1st and the 2nd power source, by there is no the power of the power source of failure to the left and right
This two side of driving wheel transmitting, and the braking torque of left and right sidesing driving wheel is controlled, the sideslip of vehicle is thus prevented, there is no need to make vehicle
Stop, even if can also ensure that the stable driving performance of vehicle in turning.
The invention of second aspect is characterized in that, in the power device of the vehicle described in first aspect, also has driving
Taking turns difference in torque computing unit, (ECU 2, the step 2) of Fig. 4 calculate left and right driving according to the target torque of the 1st and the 2nd power source
The difference of the torque of WL, WR is taken turns as drive wheel torque difference Δ T, when malfunction has occurred in the turning of vehicle, in failure shape
State occur after until passing through stipulated time (stipulated time TMREF) in a period of, target torque setup unit is by the 1st and the
The target torque TMGNG of a power source (failing motor) for being judged as having occurred failure in 2 power sources is set as 0, with
Can obtain will break down before state the mode of calculated drive wheel torque difference Δ T be judged as not having to set
The target torque TMGOK of another power source (non-faulting motor) to break down.
According to this structure, when malfunction has occurred in the turning of vehicle, to by rule after malfunction generation
The target torque that a power source of failure has occurred is set as 0 in a period of until fixing time, will be sent out with that can obtain
Before raw malfunction the mode of calculated drive wheel torque difference be configured without another power source to break down
Target torque.It is nonserviceabled after just occurring as a result, the difference in torque between left and right sidesing driving wheel is remained and event will occur
Identical state before barrier state, thereby, it is possible to carry out stable turning driving.
The invention of the third aspect is characterized in that, the power device of the vehicle described in first aspect or second aspect
In, when malfunction has occurred in the straight trip of vehicle, nonserviceable generation after to pass through the stipulated time until in a period of,
The target torque (TMGNG, TMGOK) of 1st and the 2nd power source is set as 0 by target torque setup unit.
According to this structure, when malfunction has occurred in the straight trip of vehicle, to by rule after malfunction generation
In a period of until fixing time, the target torque of the 1st and the 2nd power source is set as 0.It nonserviceables as a result, rigid generation
Later, it will not make to generate difference in torque between left and right sidesing driving wheel, can be travelled by inertia and carry out stable straight trip.
The invention of fourth aspect is characterized in that, in the power device of the vehicle described in second aspect or the third aspect,
After it have passed through the defined time, target torque setup unit will be judged as having occurred the one of failure in the 1st and the 2nd power source
The target torque TMGNG of a power source is set as 0, requires torque to be judged as that there is no failures to set according to driving wheel
The target torque TMGOK of another power source.
According to this structure, after it have passed through the defined time from the state of breaking down, one of failure will be had occurred
The target torque of power source is set as 0, requires torque to be configured without another power source to break down according to driving wheel
Target torque.Thereby, it is possible to ensure the torque of required driving wheel at the moment, and at the same time carrying out differential limiting mechanism
Differential limitation and the control for preventing the braking torque to break away, thereby, it is possible to while the torque demand for meeting driver
Carry out stable traveling.
Detailed description of the invention
Fig. 1 is the framework for showing the power device of the vehicle of the 1st embodiment of the invention together with left and right sidesing driving wheel
Figure.
Framework when Fig. 2 is the 1st pinion gear, the 2nd pinion gear and the planet carrier of the epicyclic gearing of overlook view Fig. 1
Figure.
Fig. 3 is the block diagram for showing the control device of power device together with associated device.
Fig. 4 is the flow chart for showing the dynamic Control processing executed by control device.
Fig. 5 is the equilibrium relation for showing rotation speed relation and torque between the rotary element of the power device in straight trip acceleration
Nomogram.
Fig. 6 is to show the 1st and the 2nd motor the setting there is no target torque in the case where failure in acceleration of turning right
Determine the nomogram of the relationship of the revolving speed between situation, the rotary element of power device and the equilibrium relation of torque.
Fig. 7 is the mesh shown after failure in the case that failure has occurred in the 2nd motor in acceleration of turning right just occurs
Mark the nomogram of the relationship of the revolving speed between the setting situation of torque, the rotary element of power device and the equilibrium relation of torque.
Fig. 8 is the mesh shown after failure in the case that failure has occurred in the 1st motor in acceleration of turning right just occurs
Mark the nomogram of the relationship of the revolving speed between the setting situation of torque, the rotary element of power device and the equilibrium relation of torque.
Fig. 9 is the power device shown in the case where carrying out differential limitation after Fig. 7 or Fig. 8 and sideslip prevents control
The nomogram of the equilibrium relation of the relationship and torque of revolving speed between rotary element.
Figure 10 be show turn right slow down in the 1st and the 2nd motor there is no target torques in the case where failure
The nomogram of the equilibrium relation of the relationship and torque of revolving speed between setting situation, the rotary element of power device.
Figure 11 is that the side shown after Figure 10 in the 1st and the 2nd motor breaks down, and has carried out differential limitation and side
The alignment of the equilibrium relation of the relationship and torque of revolving speed between the sliding rotary element for preventing the power device in the case where controlling
Figure.
Figure 12 is the framework for showing the power device of the vehicle of the 2nd embodiment of the invention together with left and right sidesing driving wheel
Figure.
Figure 13 is the relationship and torque of the revolving speed between the rotary element for the power device for showing Figure 12 in straight trip acceleration
Equilibrium relation nomogram.
Label declaration
1: power device
PG: epicyclic gearing (geared system)
S1: the 1 sun gear (the 1st outside rotary element)
S2: the 2 sun gear (the 2nd outside rotary element)
R1: the 1 gear ring (the 2nd inside rotary element)
R2: the 2 gear ring (the 1st inside rotary element)
51: power device
GS: geared system
S21: the 1 sun gear (the 2nd inside rotary element)
S22: the 2 sun gear (the 1st inside rotary element)
S23: the 3 sun gear (the 1st outside rotary element)
C2: planet carrier (the 2nd outside rotary element)
WL: left driving wheel
WR: right driving wheel
MG1: the 1 motor (the 1st power source)
MG2: the 2 motor (the 2nd power source)
The target torque (the 1st power source target torque) of TM1: the 1 motor
The target torque (the 2nd power source target torque) of TM2: the 2 motor
MC: differential limiting mechanism
SD: brake apparatus
Δ T: drive wheel torque is poor
TMREF: stipulated time (specified time limit)
TMGNG: the target torque (being judged as that the target torque of the power source of failure has occurred) of failing motor
TMGOK: the target torque (target torque for being judged as the power source there is no failure) of non-faulting motor
Specific embodiment
Hereinafter, being described in detail referring to attached drawing to embodiment preferred for this invention.Fig. 1 shows the 1st implementation
The power device 1 of the vehicle of mode.The power device 1 is equipped on four-wheel car (not shown), is used for the 1st motor MG1 and the 2nd
The power of motor MG2 via left and right drive shaft SL, SR, distribute and transmit to the left by right driving wheel WL, WR.
Power device 1 have above-mentioned 1st and the 2nd motor MG1, MG2, epicyclic gearing PG, differential limiting mechanism MC with
And brake apparatus SD.1st, the 2nd motor MG1, MG2 and epicyclic gearing PG and left and right drive shaft SL, SR are configured in coaxial.
1st motor MG1 is for example made of AC motor, has the 1st stator 11a, He Bao comprising multiple iron cores and coil etc.
The 1st rotor 11b containing multiple magnet etc..1st stator 11a is fixed on motionless shell CA, and the 1st rotor 11b is configured to and the 1st
Stator 11a is opposed.When supplying electric power to the 1st stator 11a, which is converted into power, exports (power to the 1st rotor 11b
Operation).In addition, the power is converted into electric power when to the 1st rotor 11b input power, and it is output to the 1st stator 11a (again
It is raw).
In addition, the 1st stator 11a is filled via the 1st Motorized drive unit (hereinafter referred to as " 1PDU ") 21 with being able to carry out
Electricity and the battery 23 of electric discharge connect, and giving and accepting for electric energy can be carried out between battery 23.As shown in figure 3,1PDU 21 and ECU
2 electrical connections.Torque (power operation torque and regeneration torsion by controlling 1PDU 21 using ECU 2, to the 1st motor MG1
Square) it is controlled.
2nd motor MG2 is constituted in a manner of same as the 1st motor MG1, has the 2nd stator 12a and the 2nd rotor 12b.It is logical
It crosses using ECU 2 and controls 2PDU 22, the torque of the 2nd motor MG2 is controlled.
Epicyclic gearing PG is used for right driving wheel WL, the WR distribution to the left of the power of the 1st and the 2nd motor MG1, MG2 simultaneously
Transmitting.Epicyclic gearing PG includes multiple 1st pinion gear P1 and the 2nd pinion gear P2；By fulcrum 13,14 respectively by these
The planet carrier C that 1st and the 2nd pinion gear P1, P2 rotatably supports；The 1st sun gear S1 engaged with multiple 1st pinion gear P1
With the 1st gear ring R1；And the 2nd sun gear S2 and the 2nd gear ring R2 engaged with multiple 2nd pinion gear P2.
As shown in Fig. 2, the 1st and the 2nd pinion gear P1, P2 is configured in the circumferential direction centered on drive shaft SL, SR that
This partly overlaps, and is intermeshed.In addition, the tooth number Z P1 of the 1st pinion gear is equal with the tooth number Z P2 of the 2nd pinion gear P2, the 1st too
The tooth number Z R1 tooth with the tooth number Z S2 and the 2nd gear ring R2 of the 2nd sun gear S2 respectively of the tooth number Z S1 and the 1st gear ring R1 of sun wheel S1
Number ZR2 is equal.
In addition, the 1st sun gear S1 is coupled via the 1st coupking shaft 15 with the rotor 11b of the 1st motor MG1, the 2nd sun gear S2
It is coupled via the 2nd coupking shaft 16 with the rotor 12b of the 2nd motor MG2, the 2nd gear ring R2 is via left driving shaft SL and left driving wheel WL
It is coupled, the 1st gear ring R1 is coupled via right driving axle SR with right driving wheel WR.In addition, being provided with halting mechanism on planet carrier C
MP.Halting mechanism MP is used to make planet carrier C lock by the operation of the gear lever (not shown) in response to vehicle, thus by vehicle
Remain parked state.
In above power device 1, epicyclic gearing PG is constituted in the above described manner, and rotary element is as described above
It is coupled with the 1st and the 2nd motor MG1, MG2, left and right sidesing driving wheel WL, WR and halting mechanism MP, therefore the revolving speed between rotary element
The relationship such as nomogram of Fig. 5 indicate like that.
That is, the 1st sun gear S1 (the rotor 11b of the 1st motor MG1), the 2nd gear ring R2 (left driving wheel WL), planet carrier C (are stayed
Mechanism of car MP), the 1st gear ring R1 (right driving wheel WR) and the 2nd sun gear S2 (the rotor 12b of the 2nd motor MG2) be configured to, it is full
Their revolving speed of foot is arranged in the alignment relationship of 1 alignment, 5 element on single straight line in the order described above in nomogram.Cause
This, as shown in figure 5, the 1st sun gear S1 and the 2nd sun gear S2 in two outsides on the nomogram are respectively equivalent to of the invention the
1 and the 2nd outside rotary element, and 2nd gear ring R2 and 1st gear ring R1 in the inner part adjacent with the 1st and the 2nd outside rotary element
It is respectively equivalent to the 1st and the 2nd inside rotary element.
In addition, the α 1 and β 1 of Fig. 5 are the 1st thick stick of on the basis of the interval of the 1st gear ring R1 of the 2nd gear ring R2- (=1) respectively
Bar rate and the 2nd leverage, using the tooth number Z of rotary element, following formula (1) and (2) are indicated.
α 1=ZR1 (ZR2-ZS1)/ZS1 (ZR2+ZR1) (1)
β 1=ZR2 (ZR1-ZS2)/ZS2 (ZR2+ZR1) (2)
In addition, as described above, in the present embodiment, tooth number Z R1, ZR2 of the 1st and the 2nd gear ring R1, R2 phase each other
Deng tooth number Z S1, ZS2 of the 1st and the 2nd sun gear S1, S2 is equal to each other, therefore the 1st and the 2nd leverage α 1, β 1 are equal to each other.
Also, tooth number Z P1, ZP2 of the 1st and the 2nd pinion gear P1, P2 is equal to each other, therefore the planet carrier C in nomogram is to the 2nd gear ring
The distance of (left driving wheel WL) is equal to each other at a distance from planet carrier C to the 1st gear ring (right driving wheel WR).
The alignment relationship of 5 element of above such 1 alignment is set up, and the 1st and the 2nd motor MG1, MG2 is linked in respectively
1st sun gear S1 (the 1st outside rotary element) and the 2nd sun gear S2 (the 2nd outside rotary element), left and right sidesing driving wheel WL, WR point
It is not linked in the 2nd gear ring R2 (the 1st inside rotary element) and the 1st gear ring R1 (the 2nd inside rotary element).Therefore, by the 1st and
The torque of 2 motor MG1, MG2 via epicyclic gearing PG, transmit to the left by right driving wheel WL, WR, and makes the 1st and the 2nd motor
The torque of MG1, MG2 are different from each other, thus make to generate difference in torque between left and right sidesing driving wheel WL, WR, are able to carry out torque distribution.
Differential limiting mechanism MC is for limiting the differential speed rotation between left and right sidesing driving wheel WL, WR.Differential limitation machine
Structure MC is for example made of the friction clutch of fluid pressure type, inner member and external member (not shown) with ring flat-plate shape.Inner member
It is linked in the 1st coupking shaft 15, the 1st coupking shaft 15 is coupled the rotor 11b and the 1st sun gear S1 of the 1st motor MG1, external member connection
It ties in the 2nd coupking shaft 16, the 2nd coupking shaft 16 is coupled the rotor 12b and the 2nd sun gear S2 of the 2nd motor MG2.
In addition, differential limiting mechanism MC is connected to hydraulic circuit 25 (referring to Fig. 3).By utilizing aftermentioned ECU2 to the liquid
Road 25 is pushed back to be controlled, to control the tightness of differential limiting mechanism MC, the 1st sun gear S1 the (the 1st as a result,
Motor MG1) and the 2nd sun gear S2 (the 2nd motor MG2) between be connected/cutting, and connection when control therebetween by
The differential limitation torque of transmitting.
Brake apparatus SD is made of the liquid braking device 26 for being respectively arranged at driving wheel WL, WR, and each liquid braking device 26 passes through
Hydraulic motor 27 (referring to Fig. 3) is connected to by hydraulic circuit (not shown).Hydraulic motor 27 is controlled using ECU 2, from
And the wheel cylinder pressure of driving wheel WL, WR are controlled, the braking torque of driving wheel WL, WR are controlled independently of one another as a result,
System.
As shown in figure 3, input indicates 4 vehicles including driving wheel WL, WR from vehicle-wheel speed sensor 31 to ECU 2
The speed of wheel, that is, wheel velocity VW1~4 detection signal, from accelerator open degree sensor 32 to ECU2, input indicates the throttle of vehicle
The detection signal of operating quantity (hereinafter referred to as " accelerator open degree ") AP of pedal (not shown).ECU 2 according to wheel velocity VW1~
4 calculate vehicle velocity V P.
In addition, from Yaw rate sensor 33 to ECU 2, input indicates the detection signal of the yaw rate Y of vehicle, from steering angle
Sensor 34 inputs the detection signal for indicating the steering angle θ of deflecting roller (not shown) of vehicle to ECU 2, passes from transverse acceleration
Sensor 35 inputs the detection signal for indicating the lateral acceleration G y of vehicle to ECU 2, from front and rear acceleration sensor 36 to ECU 2
Input indicates the detection signal of the fore-aft acceleration Gx of vehicle.Also, from current sensor 37 and voltage sensor 38 to ECU 2
The detection signal of electric current IM, voltage VM in the 1st and the 2nd motor MG1, MG2 of input expression.
ECU 2 is utilized and is made of the microcomputer of the formation such as I/O interface, CPU, RAM and ROM.ECU 2 is according to above-mentioned
The detection signal of various sensors 31~38, according to the control program stored in ROM come to the 1st and the 2nd motor MG1, MG2,
Differential limiting mechanism MC and brake apparatus SD are controlled.In the present embodiment, it is single to be equivalent to target torque setting by ECU 2
Member, malfunction judging unit, control unit and drive wheel torque difference computing unit.
Fig. 4 shows the dynamic Control processing executed by ECU 2.In dynamic Control processing, the 1st and the 2nd motor is determined
The malfunction of MG1, MG2, and according to the judgement as a result, being controlled by torque of the above-mentioned device to driving wheel WL, WR
System.Present treatment is executed repeatedly with the defined period.
In present treatment, first in step 1 (" S1 " and diagram.It is same as below) in, by according to the steering angle detected
θ, vehicle velocity V P and accelerator open degree AP etc. retrieve defined mapping graph (not shown), to calculate required by left and right sidesing driving wheel WL, WR
Driving wheel require torque, and according to the driving wheel require torque come calculate from the 1st and the 2nd motor MG1, MG2 export torsion
Target value, that is, target torque TM1, TM2 of square.
In this case, when vehicle is kept straight on and when being in constant speed drive or giving it the gun, such as shown in Fig. 5, target
Torque T M1, TM2 is calculated as tractive torque that direction is driven is marched forward to left and right sidesing driving wheel WL, WR, and is set
It is set to the value being equal to each other.Fig. 5 shows the relationship of the revolving speed between 5 rotary elements in this case and the balance of torque is closed
System.RLE and RRE in the figure are the inputs with target torque TM1, TM2 and are respectively acting on left and right sidesing driving wheel WL, WR
Reaction torque, due to target torque TM1=TM2, be equal to each other (RLE=RRE).In addition, be transmitted to left and right sidesing driving wheel WL,
The torque (hereinafter referred to as " left driving wheel torque ", " right driving wheel torque ") of WR is indicated respectively with-RLE and-RRE.Root
According to the above results, the drive wheel torque difference Δ T of the difference as left and right sidesing driving wheel torque becomes 0, by utilizing the torsion being equal to each other
Square drives left and right sidesing driving wheel WL, WR, to keep straight on.
In addition, in vehicle turns right and when giving it the gun, such as shown in Fig. 6, calculate the 1st and the 2nd motor MG1, MG2
Target torque TM1, TM2 as tractive torque, and target torque TM1 is set to the value bigger than target torque TM2.By
This, the reaction torque RLE of left driving wheel WL is bigger than the reaction torque RRE of right driving wheel WR, to generate drive wheel torque difference Δ
T.As a result, the yawing to be bent to right by generating vehicle, carries out right-hand bend traveling.
In the step 2 of the then above-mentioned steps 1 of Fig. 4, drive wheel torque difference Δ T is calculated according to target torque TM1, TM2.
Drive wheel torque difference Δ T is equal to 0 when vehicle is kept straight on as described above, is calculated in Ackermann steer angle by following formula (3).
Δ T=RLE-RRE=TM1 (1.0+2 α 1)-TM2 (1.0+2 β 1) (3)
In addition, the formula (3) be by the balance that for example indicates the torque of the left driving wheel WL in Fig. 6 following formula (4) and
(5) it is exported with expression around the following formula (6) of the balance of the torque of right driving wheel WR and (7).
RRE × 1.0+TM1 × α 1=TM2 × (1.0+ β 1) (4)
RRE=TM2 × (1.0+ β 1)-TM1 × α 1 (5)
RLE × 1.0+TM2 × β 1=TM1 × (1.0+ α 1) (6)
RLE=TM1 × (1.0+ α 1)-TM2 × β 1 (7)
Next, determining the malfunction (step 3) of the 1st and the 2nd motor MG1, MG2.The judgement is for example as follows
It carries out.Firstly, calculating motor according to the electric current IM and voltage VM etc. that are detected by current sensor 37 and voltage sensor 38
Actual torque TMA1, TMA2 of MG1, MG2 reality output.In addition, being calculated for each motor, calculated in the step 1
Torque deviation Δ TM1 (=TM1-TMA1) and Δ TM2 between target torque TM1, TM2 and actual torque TMA1, TMA2 out
(=TM2-TMA2).
Then, when the side in these torque deviation Δ TM1 and Δ TM2 is in outside prescribed limit, it is determined as the motor
Having occurred can not the functional fault such as output torque.In this case, it will indicate to have occurred the motor failure of the malfunction of motor
Mark F_MOTNG is set as " 1 ", and malfunction has occurred and makes emergency warning lamp 29 (referring to Fig. 3) point in order to alert driver
It is bright.In addition, for convenience of explanation, hereinafter, the horse of failure is had occurred in being judged as among the 1st and the 2nd motor MG1, MG2
Up to referred to as " failing motor ", will be judged as, there is no the motors of failure to be known as " non-faulting motor ".
It whether is that " 1 " differentiates to motor failure mark F_MOTNG in the then step 4 of above-mentioned steps 3.When answering
It answers as "No", there is no when motor failure state, the value TM_TDR for adding the timer of counter is reset to " 0 " (step 5),
Terminate present treatment.That is, in this case, the target for being directly used in the 1st, the 2nd motor MG1 and MG2 set in step 1 is turned round
Square TM1, TM2.
On the other hand, it is "Yes" in the response of the step 4, when the malfunction of motor has occurred, differentiates motor failure
Whether the previous value F_MOTNGZ of mark is " 1 " (step 6).When the response is "No", i.e., it is in this processing cycle
When being equivalent to after malfunction just has occurred, differentiate whether vehicle is in (step 7) in straight trip.The differentiation for example passes through
Following manner carries out: when being determined as when detected yaw rate Y is below specified value in straight trip, when detected
Yaw rate Y it is bigger than defined value when be determined as in turning in.
When differentiation result in step 7 is that vehicle is in straight trip, by the target torque TMGNG of failing motor and non-event
The target torque TMGOK of barrier motor is set as 0 (step 8,9), is transferred to subsequent steps 12.Using the setting, pass through vehicle
Inertia travel to maintain straight-going state.
In contrast, when vehicle is in turning, the target torque TMGNG of failing motor is set as 0 (step 10),
On the other hand, the target torque TMGOK (step 11) of non-faulting motor is calculated.In this case, target torque TMGOK is to take
The mode of calculated drive wheel torque difference Δ T in the step 2 is obtained to calculate.Specifically, occurring in the 2nd motor MG2
It is calculated in the case where failure using following formula (8), is counted in the case where failure has occurred in the 1st motor MG1 using following formula (9)
It calculates.
TMGOK=Δ T/ (1.0+2 α 1) (8)
TMGOK=- Δ T/ (1.0+2 β 1) (9)
Formula (8) is the target torque by making the 2nd motor MG2 in the calculating formula (3) of drive wheel torque difference Δ T above-mentioned
TM2=0, and the target torque TM1 of the 1st motor MG1 is replaced into TMGOK and derived.Equally, formula (9) is by formula (3)
In make target torque TM1=0, and target torque TM2 is replaced into TMGOK and derived.
The right-hand bend that Fig. 7 shows vehicle shown in Fig. 6 accelerate in the case that failure has occurred in the 2nd motor MG2
The setting situation of target torque TM1, TM2 of 1st and the 2nd motor MG1.In this case, by the 2nd motor as failing motor
The target torque TM2 (=TMGNG) of MG2 is set as 0, and calculates i.e. the 1st motor MG1's of non-faulting motor using formula (8)
Target torque TM1 (=TMGOK) is used as tractive torque.The driving wheel set when maintain will break down is turned round as a result,
Right-hand bend traveling is carried out in the state of square difference Δ T.
In addition, Fig. 8 shows the case where failure has occurred in 1st motor MG1 in the right-hand bend acceleration of vehicle shown in Fig. 6
Under the 1st and the 2nd motor MG1 target torque TM1, TM2 setting situation.In this case, by the 1st as failing motor
The target torque TM1 (TMGNG) of motor MG1 is set as 0, and calculates non-faulting motor i.e. the 2nd motor MG2 using formula (9)
Target torque TM2 (TMGOK) be used as regenerative torque.As a result, maintain will break down before set driving wheel
Right-hand bend traveling is carried out in the state of difference in torque Δ T.
In the then step 12 of the step 9 or step 11, the sideslip for starting to carry out vehicle prevents control (VSA control
System).The sideslip prevents control from for example proceeding as follows.Firstly, setting mesh according to the vehicle velocity V P and steering angle θ that detect
Yaw rate YCMD is marked, and calculates the target yaw rate YCMD and the actual yaw rate as detected by Yaw rate sensor 33
Deviation between Y is as yaw rate deviation Δ Y.In addition, setting target side slip angle BCMD, root according to vehicle velocity V P and steering angle θ
According to vehicle velocity V P, actual yaw rate Y and detected by lateral acceleration sensor 35 lateral acceleration G y calculates reality
Yaw angle B, and the deviation between target side slip angle BCMD and practical yaw angle B is calculated as yaw angle deviation delta B.
Then, it is assumed that when yaw rate deviation Δ Y has been more than its defined threshold value, and/or person is in yaw angle deviation delta B
The sideslip that vehicle may occur when being more than its defined threshold value, by being controlled using the liquid braking device 27 of brake apparatus SD
The braking torque of left and right sidesing driving wheel WL, WR prevent the sideslip of vehicle.
Next, so that differential limiting mechanism MC is started to work and driving to hydraulic circuit 25 in step 13,
And the differential limitation torque T DR transmitted via differential limiting mechanism MC at step 14, is set as 0, terminates present treatment.
On the other hand, it when the response in the step 6 is "Yes", i.e., is in this processing cycle and is equivalent to motor
Malfunction when having occurred that after 2 times, whether be rule to the timer value TM_TDR being reset in the step 5
The TMREF or more that fixes time is differentiated (step 15).When the response is "No", that is, without by rule after generation of nonserviceabling
Fix time TMREF when, directly terminate present treatment.That is, in this case, continuing the control of step 7~14.
It, will when the response of above-mentioned steps 15 is "Yes", has already been through stipulated time TMREF after generation of nonserviceabling
The target torque TMGNG of failing motor is set as 0 (step 16), and the target torque TMGOK of non-faulting motor is set as
The sum of set target torque TM1, TM2 of the 1st and the 2nd motor MG1, MG2 (=TM1+TM2) (step in the step 1
17)。
In addition, calculating differential limitation torque T DR according to the target torque TMGOK of non-faulting motor, such as it is set as mesh
Mark the about 1/2 (step 18) of torque T MGOK.As a result, as shown in figure 9, by the torsion of non-faulting motor (such as the 1st motor MG1)
About the 1/2 of square is transmitted to the side failing motor (such as the 2nd motor MG2) via differential limiting mechanism MC, makes to be input to left and right
The torque of driving wheel WL, WR are roughly equal.
In addition, the situation when right-hand bend that Fig. 9 shows vehicle same as Fig. 6 accelerates, is being judged to that vehicle may occur
Sideslip when, passing through to break away prevents from controlling the braking torque TBR applied to right driving wheel WR for preventing from breakking away.As a result, can
It is enough to carry out right-hand bend traveling while properly preventing and breakking away.
In the step 19 after above-mentioned steps 18, the stabilization driving status of vehicle is determined.The judgement is for example logical
It crosses and the yaw rate deviation Δ Y between target yaw rate YCMD above-mentioned and actual yaw rate Y is compared with defined threshold value
Come carry out.As a result, directly terminate present treatment in the case where the stabilization driving status of no confirmation vehicle, it is lasting to carry out
Sideslip prevents from controlling.On the other hand, in the case where confirmed the stabilization driving status of vehicle, releasing to break away prevents control (step
It is rapid 20), terminate present treatment.
In addition, as shown in Figure 10, there is no when the malfunction of motor in the Reduced Speed Now in vehicle turns right,
Target torque TM1, TM2 of the 1st and the 2nd motor MG1, MG2 is calculated as regenerative torque, and by the exhausted of target torque TM2
Value is set to bigger than the absolute value of target torque TM1.The reaction torque RRE of right driving wheel WR is than left driving wheel WL's as a result,
Reaction torque RLE is big, generates drive wheel torque difference Δ T.As a result, make the yawing of vehicle turns right by generating,
Carry out right-hand bend traveling.
It is and preceding by executing the step 10 and 11 of Fig. 4 in the case where the malfunction of motor has occurred from the state
State give it the gun in the case where identically, when failure has occurred in the 2nd motor MG2, as shown in Figure 7 set target turn round
Square TM1, TM2 set target torque TM1, TM2 as shown in Figure 8, are maintain as a result, when failure has occurred in the 1st motor MG1
Right-hand bend traveling is carried out in the state of set drive wheel torque difference Δ T before will breaking down.
In addition, as shown in Figure 11 thereafter through step 16~18 of Fig. 4 are executed, by non-faulting motor the (such as the 1st
Motor MG1) torque (regenerative torque) about 1/2 be transmitted to failing motor (such as the 2nd motor via differential limiting mechanism MC
MG2) side keeps the torque for being input to left and right sidesing driving wheel WL, WR roughly equal.Also, when the sideslip of vehicle may occur, pass through
Breakking away prevents from controlling the braking torque TBR applied to right driving wheel WR for preventing from breakking away.Even if the deceleration in turning as a result,
In traveling, turning driving can be also carried out while properly preventing the sideslip of vehicle.
As above, power device 1 according to the present embodiment, the side hair in the 1st and the 2nd motor MG1, MG2
When having given birth to failure, by making differential limiting mechanism MC work, by the power of non-faulting motor this both sides of right driving wheel WL, WR to the left
Transmitting, and controls the braking torque of driving wheel WL, WR, thus prevents the sideslip of vehicle.As a result, in the state of breaking down
When, without stopping vehicle, even if can also ensure that the stable driving performance of vehicle in turning.
In addition, when malfunction has occurred in the turning in vehicle, when after malfunction generation to by regulation
Between until TMREF in a period of, the target torque TMGNG of failing motor is set as 0, and will occur can obtain
When malfunction the mode of calculated drive wheel torque difference Δ T set the target torque TMGOK of non-faulting motor.As a result,
It nonserviceables after just occurring, the difference in torque between driving wheel WL, WR is maintained as and phase before the state that will break down
Same state, thereby, it is possible to carry out stable turning driving.
On the other hand, when malfunction has occurred in the straight trip in vehicle, to warp after the malfunction has occurred
In a period of crossing until stipulated time TMREF, by the target torque of the target torque TMGNG of failing motor and non-faulting motor
TMGOK is set as 0.It is nonserviceabled after just occurring as a result, can make not generate torque between left and right sidesing driving wheel WL, WR
Difference carries out stable straight trip by inertia traveling.
In addition, the target torque TMGNG of failing motor is set as 0 after it have passed through above-mentioned stipulated time TMREF,
And the target torque TMGOK of non-faulting motor is set as to target torque TM1, TM2 according to driving wheel requirement torque setting
The sum of.Thus, it is ensured that the torque of driving wheel WL, WR required by the moment, and at the same time carrying out based on differential limitation machine
The differential limitation of structure MC and the braking torque control that control is prevented based on sideslip, thereby, it is possible to want in the torque for meeting driver
Stable traveling is carried out while asking.
Next, the power device of the vehicle of 2 pairs of the 2nd embodiments of the invention is illustrated referring to Fig.1.Power dress
51 are set compared with the power device 1 of the 1st embodiment, by the power of the 1st and the 2nd motor MG1, MG2 to the left right driving wheel WL,
The structure of the geared system of WR transmitting is different.Therefore, in Figure 12, to the structural element identical or equivalent as the 1st embodiment
Identical symbol is marked, hereinafter, being illustrated centered on the point different from the 1st embodiment.
As shown in the drawing, the geared system GS of present embodiment includes multiple 3 company pinion gear PE；Connect pinion gear for multiple 3
The planet carrier C2 that PE is rotatably supported；With the 1st~the 3rd sun gear S21~S23.Each 3 company pinion gear PE is provided integrally with the
1~the 3rd pinion gear P21~P23, the 1st~the 3rd sun gear S21~S23 are nibbled with these the 1st~the 3rd pinion gear P21~P23 respectively
It closes.Engagement diameter RP21~RP23 of 1st~the 3rd pinion gear P21~P23 successively becomes smaller, and corresponds to this, the 1st~the 3rd sun gear
Engagement diameter RS21~RS23 of S21~S23 successively becomes larger.
In addition, the 3rd sun gear S23 is coupled, planet carrier C and the 2nd via coupking shaft 17 with the rotor 11b of the 1st motor MG1
The rotor 12b of motor MG2 is coupled, and the 2nd sun gear S22 is coupled, the 1st sun gear via left driving shaft SL with left driving wheel WL
S21 is coupled via right driving axle SR with right driving wheel WR.
In the power device 51 of above structure, the rotary element for the geared system GS for connecting pinion gear PE with 3 is for example above-mentioned
It is coupled like that with the 1st, the 2nd motor MG1, MG2 with left and right sidesing driving wheel WL, WR, therefore the rotation speed relation between rotary element is for example
It is indicated as the nomogram of Figure 13.
That is, the 3rd sun gear S23 (the rotor 11b of the 1st motor MG1), the 2nd sun gear S22 (left driving wheel WL), the 1st sun
Wheel S21 (right driving wheel WR) and planet carrier C2 (the rotor 12b of the 2nd motor MG2) are configured to, and meet their revolving speed in alignment
It is arranged successively in figure in the alignment relationship of 1 alignment, 4 element on single straight line.Therefore, as shown in figure 13, two on the nomogram
The 3rd sun gear S23 and planet carrier C2 in outside are respectively equivalent to the 1st and the 2nd outside rotary element of the invention, adjacent with them
And the 2nd gear ring S22 in the inner part and the 1st sun gear S21 are respectively equivalent to the 1st and the 2nd inside rotary element.
In addition, the α 2 and β 2 of Figure 13 are on the basis of the interval of the 1st sun gear S21 of the 2nd sun gear S22- (=1) respectively
The 1st leverage and the 2nd leverage, using rotary element tooth number Z and indicated as following formula (10) and (11).
α 2={ 1- (ZP22/ZS22) × (ZS23/ZP23) }
/{(ZP22/ZS22)×(ZS23/ZP23)-(ZP21/ZS21)×(ZS23/ZP23)}···(10)
β 2=(ZP21 × ZS22)/(ZS21 × ZP22-ZP21 × ZS22) (11)
The alignment relationship of above such 1 alignment, 4 element is set up, and the 1st and the 2nd motor MG1, MG2 respectively with the 3rd too
Sun wheel S23 (the 1st outside rotary element) and planet carrier C2 (the 2nd outside rotary element) connection, left and right sidesing driving wheel WL, WR respectively with
2nd sun gear S22 (the 1st inside rotary element) and the 1st sun gear S21 (the 2nd inside rotary element) is coupled.
In addition, differential limiting mechanism MC, which is arranged in, is coupled the 1st rotor 11b of motor MG1 and being coupled for the 3rd sun gear S23
Between axis 17 and the planet carrier C2 of rotor 12b for being linked in the 2nd motor MG2.
As previously discussed, in the power device of present embodiment 51, the alignment of 1 alignment, 4 element in geared system GS
Relationship is set up, and on the other hand the 1st and the 2nd motor MG1, MG2 is wanted with the 1st and the 2nd outside rotation in these rotary elements respectively
Element is coupled, and left and right sidesing driving wheel WL, WR are coupled with the 1st and the 2nd inside rotary element in these rotary elements respectively, in the 1st He
It is provided between 2nd outside rotary element in this relationship of differential limiting mechanism, it is complete with the power device 1 of the 1st embodiment
It is identical.
Therefore, it is handled, can equally be obtained above-mentioned by the dynamic Control that the power device 51 to the structure executes Fig. 4
The movement and effect of 1st embodiment.
In addition, can implement in various ways the present invention is not limited to illustrated embodiment.For example, conduct
Geared system, the epicyclic gearing for the type for having used the 1st and the 2nd pinion gear P1, P2 to engage in the 1st embodiment, and
In the 2nd embodiment, used by 3 connect pinion gear PE, with this 3 connect pinion gear PE engage multiple sun gear S21~S23,
And the geared system of type that planet carrier C2 etc. is combined.The present invention is not limited thereto, as long as 1 alignment, 5 element or 1
The alignment relationship of 4 element of alignment is set up, and multiple rotary element and the 1st and the 2nd motor MG1, MG2 and driving wheel WL,
Connection relationship between WR meets necessary condition of the invention, then can also use the geared system of other structures.
In addition, in the dynamic Control processing of Fig. 4, when have passed through regulation from the time of the malfunction of motor occurs
Between TMREF at the time of, the control of step 16~18 has been switched to from the control of step 8~11, but not limited to this, such as
It can be controlled at the time of confirmed starting according to the starting to monitor differential limiting mechanism MC such as hydraulic of hydraulic circuit 25
The switching of system.Also, it in the processing of the dynamic Control of Fig. 4, releases and is sending out at the time of the driving stability state that confirmed vehicle
The sideslip started when the malfunction of raw motor prevents from controlling, and but not limited to this, such as can also persistently carry out breakking away anti-
It only controls until the malfunction of motor is eliminated.
In addition, although in embodiments, differential limiting mechanism MC is made of the friction clutch of fluid pressure type,
It, can also be with as long as being able to carry out switching and the differential limitation torque of change of the cutting of transmitting and the power transmitting of power
It is made of the structure other than the other kinds of clutch such as electromagnetic type and clutch.
Also, in embodiments, the power source of power device is motor, but also can be used and be capable of output power
Other devices, such as internal combustion engine or hydraulic motor etc..It, can be in the range of the purport of the present invention to discreet portions about other
Structure suitably changed.
Claims (4)
1. the power device of a kind of power device of vehicle, the vehicle is passed to the left and right sidesing driving wheel that can carry out differential speed rotation each other
Graduating power,
It is characterized in that, the power device of the vehicle includes
1st power source and the 2nd power source；And
Geared system has the multiple rotary elements constituted by 4 or 5, and the multiple rotary element is configured to,
Meet the alignment relationship that revolving speed is arranged on single straight line in nomogram,
In the multiple rotary element of the geared system, the 1st outside rotation in two outsides is located in the nomogram
Element and the 2nd outside rotary element are coupled with the 1st power source and the 2nd power source respectively, in the nomogram be located at
The 1st outside rotary element and the 2nd outside rotary element is adjacent and position in the inner part on the 1st inside rotary element and
2 inside rotary elements are coupled with the left and right sidesing driving wheel respectively,
The power device of the vehicle includes
Target torque setup unit requires torque to set the described 1st according to driving wheel required by the left and right sidesing driving wheel
The target torque of power source and the 2nd power source；
Differential limiting mechanism is used for by being attached between the 1st outside rotary element and the 2nd outside rotary element
To limit the differential of the left and right sidesing driving wheel；
Brake apparatus brakes the left and right sidesing driving wheel independently of one another；
Malfunction judging unit, whether to producing malfunction and determining, which is the 1st power source
The state of functional fault has occurred with the side in the 2nd power source；And
Control unit, when being judged to that the malfunction has occurred, the control unit is by making the differential limiting mechanism work
Make and applies to being attached between the 1st outside rotary element and the 2nd outside rotary element, and to the brake apparatus
The sideslip to prevent the vehicle is controlled to the braking torque of the left and right sidesing driving wheel.
2. the power device of vehicle according to claim 1, which is characterized in that
The power device of the vehicle also has drive wheel torque difference computing unit, and the drive wheel torque difference computing unit is according to
The difference for the torque that the target torque of 1st power source and the 2nd power source calculates the left and right sidesing driving wheel is poor as drive wheel torque,
When the malfunction has occurred in the turning in vehicle, when extremely passing through defined after malfunction generation
Between until in a period of, the target torque setup unit will be judged as sending out among the 1st power source and the 2nd power source
The target torque for having given birth to a power source of failure is set as 0, is calculated before the malfunction will occur with that can obtain
The mode for the drive wheel torque difference haveing, which is set, is judged as that there is no the target torques of another of failure power source.
3. the power device of vehicle according to claim 1 or 2, which is characterized in that
When the malfunction has occurred in the straight trip in vehicle, when extremely passing through defined after malfunction generation
Between until in a period of, the target torque setup unit sets the target torque of the 1st power source and the 2nd power source
It is 0.
4. the power device of vehicle according to claim 2 or 3, which is characterized in that
Have passed through it is described as defined in after the time, the target torque setup unit is by the 1st power source and the 2nd power source
In the target torque for being judged as having occurred a power source of failure be set as 0, according to the driving wheel require torque come
Setting is judged as that there is no the target torques of another of failure power source.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018048248A JP2019158070A (en) | 2018-03-15 | 2018-03-15 | Vehicle power apparatus |
| JP2018-048248 | 2018-03-15 |
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| CN110271413A true CN110271413A (en) | 2019-09-24 |
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| CN201910163042.XA Pending CN110271413A (en) | 2018-03-15 | 2019-03-05 | The power device of vehicle |
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| DE102021006012A1 (en) * | 2021-12-06 | 2023-06-07 | Mercedes-Benz Group AG | Electrical drive system for a motor vehicle |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006256454A (en) * | 2005-03-16 | 2006-09-28 | Nissan Motor Co Ltd | Torque distribution control device of vehicle |
| JP2011131633A (en) * | 2009-12-22 | 2011-07-07 | Honda Motor Co Ltd | Yaw moment controller for vehicle |
| JP2013255357A (en) * | 2012-06-07 | 2013-12-19 | Jtekt Corp | Travelling device for vehicle |
| WO2014188923A1 (en) * | 2013-05-20 | 2014-11-27 | 日産自動車株式会社 | Vehicle behavior control device |
| CN106965800A (en) * | 2015-11-20 | 2017-07-21 | 丰田自动车株式会社 | Motor vehicle driven by mixed power |
| JP2017150616A (en) * | 2016-02-26 | 2017-08-31 | Ntn株式会社 | Device for driving right and left wheels |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014188923A (en) * | 2013-03-28 | 2014-10-06 | Japan Polyethylene Corp | Laminate film |
| JP6642517B2 (en) * | 2017-05-16 | 2020-02-05 | トヨタ自動車株式会社 | Driving force control device |
-
2018
- 2018-03-15 JP JP2018048248A patent/JP2019158070A/en active Pending
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2019
- 2019-03-05 CN CN201910163042.XA patent/CN110271413A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006256454A (en) * | 2005-03-16 | 2006-09-28 | Nissan Motor Co Ltd | Torque distribution control device of vehicle |
| JP2011131633A (en) * | 2009-12-22 | 2011-07-07 | Honda Motor Co Ltd | Yaw moment controller for vehicle |
| JP2013255357A (en) * | 2012-06-07 | 2013-12-19 | Jtekt Corp | Travelling device for vehicle |
| WO2014188923A1 (en) * | 2013-05-20 | 2014-11-27 | 日産自動車株式会社 | Vehicle behavior control device |
| CN106965800A (en) * | 2015-11-20 | 2017-07-21 | 丰田自动车株式会社 | Motor vehicle driven by mixed power |
| JP2017150616A (en) * | 2016-02-26 | 2017-08-31 | Ntn株式会社 | Device for driving right and left wheels |
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