CN106195193B - A kind of planetary electric differential mechanism of double clutch - Google Patents
A kind of planetary electric differential mechanism of double clutch Download PDFInfo
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- CN106195193B CN106195193B CN201610880478.7A CN201610880478A CN106195193B CN 106195193 B CN106195193 B CN 106195193B CN 201610880478 A CN201610880478 A CN 201610880478A CN 106195193 B CN106195193 B CN 106195193B
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- planetary gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
Abstract
The invention discloses a kind of planetary electric differential mechanism of double clutch, it is related to automobile technical field, including main differential mechanism, dual planetary gear planet row, the left planet row of torque distribution, the right planet row of torque distribution, reduction planetary row, power clutch, torque distribution clutch and motor；The switching of different working modes can be realized with separating by controlling torque to distribute the engagement of clutch and power clutch.Structure design of the present invention is compact, solves automobile pass through poor performance on bad road surface the defects of, realizes the fixed direction allocation of drive shaft output torque；Solve the problems, such as that automobile is limited in low regime accelerating ability difference and climbing capacity, improve the dynamic property and economy of automobile.
Description
Technical field
The present invention relates to automobile technical field, more particularly to a kind of planetary electric differential mechanism of double clutch.
Background technology
One of the critical component of differential mechanism as automobile, when automobile in turning driving or uneven road surface when driving, can make
Driving wheels are rolled with different angular speed, so as to ensure to make PURE ROLLING between two side drive wheels and ground.It is conventional poor
The mean allocation torque usually between two driving wheels of fast device, when one side drive wheel of automobile is in the relatively low road surface of attachment coefficient,
Such as ice and snow or muddy road surface, the side wheel driving torque very little, the characteristic of differential mechanism mean allocation torque can drive opposite side
Driving wheel tends to transfixion.Limited slip differential can solve the problems, such as to a certain extent it is this, but need it is a set of have can
By the high diff lock of precision, processing and R＆D costs are added.
With the fast development of automobile industry, following automobile will gradually tend to mixed dynamicization and motorized.Meanwhile in order to suitable
The sustainable development of environment is answered, automobile should have lower CO2 emission and energy consumption.Motor is applied to as auxiliary power
Microring array and Weak hybrid power automobile, are accepted by more and more automobile vendors, it, can as a kind of inexpensive oil-saving scheme
With effectively evade conventional hybrid system configuration it is complicated and to power of motor requirement it is high the shortcomings that.Power motor conduct
Auxiliary power of car system, can be coupled the torque of output on differential casing with engine output torque, so that
Form parallel connection type hybrid power system；The system can be not only operated alone by engine or motor, can also be joined by both
Close driving vehicle.
Therefore, it is necessary on the basis of conventional carrier, design is a kind of to have torque distribution and auxiliary power output concurrently
Electric differential mechanism.
At present, the patent of existing electric differential mechanism only introduces the torque distribution function of motor mostly, does not send out fully
Wave the power torque output function and energy recovery function of motor；Meanwhile such patent motor is generally in tempo turn and attachment
Play a role on the road surface of condition difference, motor utilization ratio is relatively low.Such as Chinese patent publication No. CN104675951A, date of publication
2015-06-03, discloses the electric differential mechanism with two-row planetary gear torque fixed direction allocation mechanism, which only considers
Torque fixed direction allocation is carried out using motor, does not play the power performance and energy regenerating of motor.A kind of double clutch is planetary
Electric differential mechanism is integrated with motor and conventional carrier, on the one hand can realize the fixed direction allocation of differential mechanism torque, effectively carry
High handling capacity and tempo turn ability of the automobile on bad road surface；The torque output of another aspect motor can be carried effectively
High vehicle reduces automobile noise, possesses the comprehensive operation efficiency of higher in the accelerating ability and grade climbing performance on straight road surface.
The content of the invention
The present invention is to overcome automobile in low regime accelerating ability difference and to be climbed by poor performance and vehicle on bad road surface
A kind of the problem of slope ability is limited, there is provided planetary electric differential mechanism of double clutch.
In order to solve the above technical problems, the present invention adopts the following technical scheme that realization, with reference to attached drawing：Described one kind
The planetary electric differential mechanism of double clutch, including main differential mechanism；The system further includes dual planetary gear planet row, torque distribution left lateral
Star row, torque distribute right planet row, reduction planetary row, power clutch, torque distribution clutch and motor；The double-planet
Wheel planet row is sleeved on the left end of right axle shaft 8, and torque distributes the right axle shaft 8 that left planet row is sleeved on the right side of dual planetary gear planet row
It is upper to distribute right planet row for rotation connection, torque and be sleeved on right axle shaft 8, torque distribution right lateral star seniority among brothers and sisters carrier 23 and right axle shaft
8 connect for spline pair, and reduction planetary arranges the right end for being sleeved on right axle shaft 8；The active part and reduction planetary of power clutch 30
Seniority among brothers and sisters carrier 27 is structure as a whole, and the secondary part of power clutch 30 is fixed on the right end of differential carrier 5, with differential carrier 5
Common rotation；Active part and the reduction planetary of torque distribution clutch 29 rank carrier 27 and are structure as a whole, torque distribute from
The secondary part of clutch 29 is fixed on the right end that torque distributes right planet row sun gear 21, and right planet row sun gear is distributed with torque
21 common rotations；The housing of motor 2 is fixed on Driving axle housing, and the rotor of motor 2 is sleeved on the right end of right axle shaft 8, with subtracting
Fast planet row sun gear 25 is rotation connection.
The planetary electric differential mechanism of a kind of double clutch provided according to the present invention, wherein, it is left half axle 7, right axle shaft 8, double
Planetary gear planet row, torque distribute left planet row, the right planet row of torque distribution, reduction planetary row, power clutch 30, torque point
Rotation conllinear with clutch 29 Yu motor 2.
The planetary electric differential mechanism of a kind of double clutch provided according to the present invention, wherein, power clutch 30 includes
Active part and secondary part, active part are structure as a whole with reduction planetary seniority among brothers and sisters carrier 27, and secondary part is fixed on differential
The right end of device shell 5；By engaging the active part and secondary part of power clutch 30, so as to fulfill the conversion of dynamic mode；
Different according to the input form of power, dynamic mode is divided into electric-only mode, pattern is operated alone in engine, joint driving mould
Formula and braking mode.
The planetary electric differential mechanism of a kind of double clutch provided according to the present invention, wherein, torque distribution clutch 29 wraps
Active part and secondary part are included, active part is structure as a whole with reduction planetary seniority among brothers and sisters carrier 27, and secondary part is fixed on
Torque distributes the right end of right planet row sun gear 21；The active part and secondary part of clutch 29 are distributed by engagement torque,
So as to fulfill the conversion of torque allocation model.
The planetary electric differential mechanism of a kind of double clutch provided according to the present invention, wherein, dual planetary gear planet row includes
Dual planetary gear planet row sun gear 12, the first planetary gear of dual planetary gear planet row 13, the second planetary gear of dual planetary gear planet row 14,
Dual planetary gear planet row gear ring 15, dual planetary gear planet row planet carrier 16；Dual planetary gear planet row sun gear 12, dual planetary gear row
Star ranked first planetary gear 13, the second planetary gear of dual planetary gear planet row 14, dual planetary gear planet row gear ring 15 and engage successively, duplicate rows
Star-wheel planet row planet carrier 16 respectively with the second planetary gear of the first planetary gear of dual planetary gear planet row 13 and dual planetary gear planet row
14 be rotation connection；Dual planetary gear planet row gear ring 15 is structure as a whole with differential carrier 5.
The planetary electric differential mechanism of a kind of double clutch provided according to the present invention, wherein, torque distributes left planet row bag
Include torque distribute left planet row sun gear 17, torque distribution left lateral star seniority among brothers and sisters star-wheel 18, torque distribution left lateral star seniority among brothers and sisters carrier 19,
Torque distribution left lateral star toothrow circle 20；Torque distributes left planet row sun gear 17, torque distribution left lateral star seniority among brothers and sisters star-wheel 18, torque
Distribution left lateral star toothrow circle 20 engages successively, torque distribution left lateral star seniority among brothers and sisters carrier 19 and torque distribution left lateral star seniority among brothers and sisters star-wheel 18
For rotation connection；Torque distribution left lateral star seniority among brothers and sisters carrier 19 is structure as a whole with dual planetary gear planet row planet carrier 16, torque point
It is structure as a whole with left planet row sun gear 17 and dual planetary gear planet row sun gear 12.
The planetary electric differential mechanism of a kind of double clutch provided according to the present invention, wherein, torque distributes right planet row bag
Include torque distribute right planet row sun gear 21, torque distribution right lateral star seniority among brothers and sisters star-wheel 22, torque distribution right lateral star seniority among brothers and sisters carrier 23,
Torque distribution right lateral star toothrow circle 24；Torque distributes right planet row sun gear 21, torque distribution right lateral star seniority among brothers and sisters star-wheel 22, torque
Distribution right lateral star toothrow circle 24 engages successively, torque distribution right lateral star seniority among brothers and sisters carrier 23 and torque distribution right lateral star seniority among brothers and sisters star-wheel 22
For rotation connection；Torque distribution right lateral star toothrow circle 24 is structure as a whole with torque distribution left lateral star toothrow circle 20.
The planetary electric differential mechanism of a kind of double clutch provided according to the present invention, wherein, reduction planetary row includes slowing down
Planet row sun gear 25, reduction planetary seniority among brothers and sisters star-wheel 26, reduction planetary seniority among brothers and sisters carrier 27, reduction planetary toothrow circle 28；Slow down row
Star row sun gear 25, reduction planetary seniority among brothers and sisters star-wheel 26, reduction planetary toothrow circle 28 engage successively, reduction planetary seniority among brothers and sisters carrier 27 with
Reduction planetary seniority among brothers and sisters star-wheel 26 is rotation connection；Reduction planetary toothrow circle 28 is fixed on Driving axle housing.
The planetary electric differential mechanism of a kind of double clutch is divided into conventional differentials pattern, torque allocation model and moves
Force mode, wherein dynamic mode are divided into electric-only mode according to the input form of power, pattern is operated alone in engine, joint
Drive pattern and braking mode.
Compared with prior art, the present invention have the beneficial effect that：
1. separation and torque that the planetary electric differential mechanism of a kind of double clutch of the present invention passes through power clutch
The engagement of clutch is distributed, opens torque allocation model, electric differential mechanism has the function of torque distribution at this time, by controlling electricity
The forward or reverse of machine rotor can give left and right semiaxis with fixed direction allocation torque, so as to improve handling capacity of the automobile on bad road surface
With tempo turn ability.
2. engagement and torque that the planetary electric differential mechanism of a kind of double clutch of the present invention passes through power clutch
The separation of clutch is distributed, turn on the power pattern, reduction planetary seniority among brothers and sisters carrier is fixed together with differential carrier, in power mould
According to the rational pattern switching of progress is actually needed under formula, the dynamic property and economy of vehicle can be effectively improved.
3. the planetary electric differential mechanism of a kind of double clutch of the present invention can be expired with the engine of selection of small power
The normally travel requirement of sufficient vehicle, reduces harmful gas emission, reduces the pollution to environment.
4. the planetary electric differential mechanism of a kind of double clutch of the present invention can reduce brake access times and
Intensity, extends its service life, reduces its maintenance, upkeep cost.
5. the planetary electric differential mechanism of a kind of double clutch of the present invention has a wide range of application, act not only as aiding in
Power set are applied in traditional passenger car and commercial car, can also be applied on pure electric automobile and hybrid vehicle.
6. the planetary electric differential mechanism of a kind of double clutch of the present invention arranges motor in coaxial fashion, structure is tight
Gather；Change to conventional carrier is smaller, and improvement cost is low.
Brief description of the drawings
The invention will be further described below in conjunction with the accompanying drawings：
Fig. 1 is a kind of structure principle chart of the planetary electric differential mechanism of double clutch of the present invention；
Fig. 2 is that dual planetary gear planet row structure cuts open in a kind of planetary electric differential mechanism of double clutch of the present invention
View；
Fig. 3 is that a kind of structure of the planetary electric differential mechanism of double clutch of the present invention under torque allocation model is former
Reason figure；
Fig. 4 is a kind of torque flow of the planetary electric differential mechanism of double clutch of the present invention under conventional differentials pattern
Dynamic path schematic diagram；
Fig. 5 torque distribution dresses under left-hand bend operating mode for a kind of planetary electric differential mechanism of double clutch of the present invention
Put the torque flowing path schematic diagram of distribution；
Fig. 6 is a kind of structural principle of the planetary electric differential mechanism of double clutch of the present invention under dynamic mode
Figure；
Fig. 7 is that a kind of driving force of the planetary electric differential mechanism of double clutch of the present invention under electric-only mode passes
Pass route schematic diagram；
Fig. 8 is a kind of planetary electric differential mechanism of double clutch of the present invention in the case where pattern is operated alone in engine
Driving force transfer route schematic diagram；
Fig. 9 is a kind of driving force of the planetary electric differential mechanism of double clutch of the present invention in the case where combining drive pattern
Transfer route schematic diagram；
Figure 10 is a kind of regeneration of planetary electric differential mechanism of double clutch of the present invention in a regenerative braking mode
Brake force transfer route schematic diagram；
In figure：1. power input shaft, 2. motors, 3. drive bevel gears, 4. driven wheel of differential, 5. differential carriers, 6. planets
Gear shaft, 7. left half axles, 8. right axle shafts, 9. left half axle bevel gears, 10. right axle shaft bevel gears, 11. bevel planet gears, 12. duplicate rows
Star-wheel planet row sun gear, 13. the first planetary gears of dual planetary gear planet row, 14. the second planetary gears of dual planetary gear planet row, 15.
Dual planetary gear planet row gear ring, 16. dual planetary gear planet row planet carriers, 17. torques distribute left planet row sun gear, 18. torques
Distribute left lateral star seniority among brothers and sisters star-wheel, 19. torques distribution left lateral star seniority among brothers and sisters carrier, 20. torques distribution left lateral star toothrow circle, 21. torques
Distribute right planet row sun gear, 22. torques distribution right lateral star seniority among brothers and sisters star-wheel, 23. torques distribution right lateral star seniority among brothers and sisters carrier, 24. turns
Square distributes right lateral star toothrow circle, 25. reduction planetaries row's sun gear, 26. reduction planetaries seniority among brothers and sisters star-wheel, 27. reduction planetary rows of planetary
Frame, 28. reduction planetary toothrow circles, 29. torques distribution clutch, 30. power clutch.
Embodiment
The present invention is explained in detail below in conjunction with the accompanying drawings：
Refering to Fig. 1, Fig. 2, Fig. 3, Fig. 6, the present invention provides a kind of planetary electric differential mechanism of double clutch, described one
The planetary electric differential mechanism of kind double clutch mainly distributes left planet row including main differential mechanism, dual planetary gear planet row, torque, turns
Square distributes right planet row, reduction planetary row, power clutch, torque distribution clutch and motor.
Refering to Fig. 1, Fig. 3, Fig. 6, the main differential mechanism includes power input shaft 1, drive bevel gear 3, from mantle tooth
Wheel 4, differential carrier 5, planetary gear shaft 6, left half axle 7, right axle shaft 8, left half axle bevel gear 9, right axle shaft bevel gear 10, planet cone
Gear 11.
Refering to Fig. 1, Fig. 3, Fig. 6, the power input shaft 1 is structure as a whole with drive bevel gear 3, passes through active conical tooth
Wheel 3 is engaged with 4 gear pair of driven wheel of differential inputs differential carrier 5 by power torque；The drive bevel gear 3 is circular cone tooth
Wheel, passes to driven wheel of differential 4 by the torque that power input shaft 1 inputs and changes the direction of transfer of torque；The slave mantle
Gear 4 is conical gear, is along the circumferential direction provided with several threaded holes, is solidly fixed with differential carrier 5 by bolt；It is described
Differential carrier 5 be thin-wall case structure, housing left end is provided with unthreaded hole, on the inside of housing right end with dual planetary gear planet row gear ring 15
It is structure as a whole, is structure as a whole with 30 secondary part of power clutch on the outside of housing right end, is along the circumferential direction opened among housing
There is unthreaded hole；The planetary gear shaft 6 is cross axle structure；The left half axle 7 and the rotation conllinear of right axle shaft 8, it is left
The right end of semiaxis 7 and the left end of right axle shaft 8 are provided with external splines, and 8 center section of right axle shaft is provided with external splines；The left half axle cone
Gear 9 and right axle shaft bevel gear 10 are conical gear, and internal spline is provided with gear；The bevel planet gear 11 is circular cone tooth
Wheel construction.
Refering to Fig. 1, Fig. 3, Fig. 6, for 1 front end of power input shaft by bearings on Driving axle housing, rear end passes through master
Dynamic bevel gear 3 is supported on 4 gear teeth of driven wheel of differential；Drive bevel gear 3 is often engaged with driven wheel of differential 4；Driven wheel of differential 4 with
Differential carrier 5 is solidly fixed by bolt；For 5 left end of differential carrier by bearings on the axle journal of left half axle 7, housing is right
End is often engaged by dual planetary gear planet row gear ring 15 with the second planetary gear of dual planetary gear planet row 14, circumferentially square among housing
To unthreaded hole be sleeved on the axle journal of planetary gear shaft 6；7 left end of left half axle by bearings on 5 housing of differential carrier, it is right
End is connected by external splines with the internal spline of left half axle bevel gear 9；8 right end of right axle shaft is by bearings in dual planetary gear planet
Arrange sun gear 12 and torque is distributed on the endoporus of right planet row sun gear 21, left end passes through external splines and right axle shaft bevel gear 10
Internal spline connects, and the internal spline that center section distributes right lateral star seniority among brothers and sisters carrier 23 by external splines with torque is connected；Left half axle is bored
Gear 9 and right axle shaft bevel gear 10 are often engaged with bevel planet gear 11 by the gear teeth, and by adjusting gasket come adjust the gear teeth it
Between gap；Bevel planet gear 11 is connected by unthreaded hole with the axle journal of planetary gear shaft 6, and is distributed on the circle of planetary gear shaft 6
In circumferential direction.
Refering to Fig. 1, Fig. 2, Fig. 3, the dual planetary gear planet row includes dual planetary gear planet row sun gear 12, duplicate rows
The first planetary gear of star-wheel planet row 13, the second planetary gear of dual planetary gear planet row 14, dual planetary gear planet row gear ring 15, double-planet
Take turns planet row planet carrier 16.
Refering to Fig. 1, Fig. 2, Fig. 3, the dual planetary gear planet row sun gear 12 is roller gear structure, is distributed with torque
Left planet row sun gear 17 is structure as a whole；First planetary gear of dual planetary gear planet row 13 is roller gear structure；Institute
The second planetary gear of dual planetary gear planet row 14 stated is roller gear structure；The dual planetary gear planet row gear ring 15 is cylinder
Inner gear structure, is structure as a whole with differential carrier 5；The dual planetary gear planet row planet carrier 16 is circular ring structure, with turning
Square distribution left lateral star seniority among brothers and sisters carrier 19 is structure as a whole.
Refering to Fig. 1, Fig. 2, Fig. 3, dual planetary gear planet row sun gear 12 is by bearings in the optical axis portion of right axle shaft 8
Point, often engaged with the first planetary gear of dual planetary gear planet row 13, with dual planetary gear planet row the second planetary gear 14 without meshing relation；
The first planetary gear of dual planetary gear planet row 13 respectively with the second row of dual planetary gear planet row sun gear 12 and dual planetary gear planet row
Star-wheel 14 often engages, with dual planetary gear planet row gear ring 15 without meshing relation；The second planetary gear of dual planetary gear planet row 14 is distinguished
Often engaged with the first planetary gear of dual planetary gear planet row 13 and dual planetary gear planet row gear ring 15；Dual planetary gear planet row gear ring 15
Often engaged with the second planetary gear of dual planetary gear planet row 14；Dual planetary gear planet row planet carrier 16 passes through axis pin and dual planetary gear row
Star ranked first planetary gear 13 and the second planetary gear of dual planetary gear planet row 14 connects, and public around dual planetary gear planet row sun gear 12
Turn.
Refering to Fig. 1, Fig. 3, the torque distributes left planet row and includes the left planet row sun gear 17 of torque distribution, torque
Distribute left lateral star seniority among brothers and sisters star-wheel 18, torque distribution left lateral star seniority among brothers and sisters carrier 19, torque distribution left lateral star toothrow circle 20.
Refering to Fig. 1, Fig. 3, it is roller gear structure that the torque, which distributes left planet row sun gear 17, with dual planetary gear row
Star row's sun gear 12 is structure as a whole；The torque distribution left lateral star seniority among brothers and sisters star-wheel 18 is roller gear structure；Described turns
Square distribution left lateral star seniority among brothers and sisters carrier 19 is circular ring structure, is structure as a whole with dual planetary gear planet row planet carrier 16；Described turns
Square distribution left lateral star toothrow circle 20 is cylinder inner gear ' structure, is structure as a whole with torque distribution right lateral star toothrow circle 24.
Refering to Fig. 1, Fig. 3, torque distribute left planet row sun gear 17 by bearings right axle shaft 8 optical axis portion,
Often engaged with torque distribution left lateral star seniority among brothers and sisters star-wheel 18；Torque distribution left lateral star seniority among brothers and sisters star-wheel 18 distributes left lateral star with torque respectively
Row's sun gear 17 and torque distribution left lateral star toothrow circle 20 often engage；Torque distribution left lateral star seniority among brothers and sisters carrier 19 is by axis pin with turning
Square distribution left lateral star seniority among brothers and sisters star-wheel 18 connects, and distributes left planet row sun gear 17 around torque and revolve round the sun.
Refering to Fig. 1, Fig. 3, the torque distributes right planet row and includes the right planet row sun gear 21 of torque distribution, torque
Distribute right lateral star seniority among brothers and sisters star-wheel 22, torque distribution right lateral star seniority among brothers and sisters carrier 23, torque distribution right lateral star toothrow circle 24.
Refering to Fig. 1, Fig. 3, it is roller gear structure that the torque, which distributes right planet row sun gear 21, with torque distribute from
Clutch 29 is structure as a whole；The torque distribution right lateral star seniority among brothers and sisters star-wheel 22 is roller gear structure；The torque distribution
Right lateral star seniority among brothers and sisters carrier 23 is circular ring structure, and circle ring center is provided with internal spline；The torque distributes right lateral star toothrow circle 24
Cylinder inner gear ' structure, is structure as a whole with torque distribution left lateral star toothrow circle 20.
Refering to Fig. 1, Fig. 3, torque distribute right planet row sun gear 21 by bearings right axle shaft 8 optical axis portion,
Left end gear parts are often engaged with torque distribution right lateral star seniority among brothers and sisters star-wheel 22；Torque distribution right lateral star seniority among brothers and sisters star-wheel 22 is respectively with turning
Square distributes right planet row sun gear 21 and torque distribution right lateral star toothrow circle 24 often engages；Torque distribution right lateral star seniority among brothers and sisters carrier 23
Right lateral star seniority among brothers and sisters star-wheel 22 is distributed by axis pin with torque to be connected, center internal spline coordinates with 8 external splines of right axle shaft, with right axle shaft
8 are rotated with same rotational speed.
Refering to Fig. 1, Fig. 3, reduction planetary row includes reduction planetary row sun gear 25, reduction planetary seniority among brothers and sisters star-wheel
26th, reduction planetary seniority among brothers and sisters carrier 27, reduction planetary toothrow circle 28.
Refering to Fig. 1, Fig. 3, reduction planetary row's sun gear 25 is roller gear structure, and the rotor with motor 2 is one
Body structure；The reduction planetary seniority among brothers and sisters star-wheel 26 is roller gear structure；The reduction planetary seniority among brothers and sisters carrier 27 is annulus
Structure, is structure as a whole with the active part of torque distribution clutch 29 and the active part of power clutch 30；Described subtracts
Fast planet row gear ring 28 is cylinder inner gear ' structure, is fixed on Driving axle housing.
Refering to Fig. 1, Fig. 3, reduction planetary arranges sun gear 25 by bearings in the optical axis portion of right axle shaft 8, left end tooth
Often engaged with reduction planetary seniority among brothers and sisters star-wheel 26 wheel part；Reduction planetary seniority among brothers and sisters star-wheel 26 respectively with reduction planetary arrange sun gear 25 and
Reduction planetary toothrow circle 28 often engages；Reduction planetary is ranked carrier 27 and is connected by axis pin with reduction planetary seniority among brothers and sisters star-wheel 26, left
The active part of end connection power clutch 29, the active part of right end connection torque distribution clutch 29.
Refering to Fig. 1, the power clutch 30 is multi-plate friction clutch, its active part is ranked with reduction planetary
Carrier 27 is structure as a whole, and secondary part is fixed together with differential carrier 5, and power clutch is engaged by rubbing action
30, so as to fulfill dynamic mode.
Refering to Fig. 1, torque distribution clutch 29 is multi-plate friction clutch, its active part and reduction planetary
Seniority among brothers and sisters carrier 27 is structure as a whole, and secondary part distributes right planet row sun gear 21 with torque and is fixed together, and is made by rubbing
Clutch 30 is distributed for engagement torque, so as to fulfill torque allocation model.
Refering to Fig. 1, Fig. 3, Fig. 6, the motor 2 is permasyn morot, and the housing of motor 2 is connected in driving axle housing
On body, motor output shaft is hollow shaft, and by bearings in the optical axis portion of right axle shaft 8, rotor and reduction planetary are arranged
Sun gear 25 is structure as a whole；By motor forward or reverse, realize torque fixed direction allocation to right axle shaft 8 or left half axle 7.Work
Make principle to divide with operating mode
Refering to Fig. 1, Fig. 3, Fig. 6, the planetary electric differential mechanism of a kind of double clutch has two power inputs, is
Engine and motor 2；The power of engine is inputted by power input shaft 1, and the power of motor 2 arranges sun gear by reduction planetary
25 inputs.
1st, conventional differentials pattern
Refering to Fig. 1, figure, 3, Fig. 4, torque distribution clutch 29 and separating force clutch 30 are in discrete state, motor
Controller control motor does not work, and realizes conventional differentials pattern.
Refering to Fig. 1, Fig. 3, Fig. 4, in good straight road traveling, electric machine controller control motor is in the shape that do not work
State, motor are exported without torque.Engine input torque is inputted from power input shaft 1, by drive bevel gear 3 and driven wheel of differential
4 engagement is delivered on differential carrier 5, and then differential carrier 5 drives planetary gear shaft 6 to be rotated along axis X, rotating planet tooth
Wheel shaft 6 drives bevel planet gear 11 thereon to be rotated along axis X, finally by bevel planet gear 11 and left half axle bevel gear 9 and
The engagement of right axle shaft bevel gear 10, transmits torque on left half axle 7 and right axle shaft 8.At this time, dual planetary gear planet toothrow
Circle 15 is rotated with differential carrier 5 with identical rotating speed, and dual planetary gear planet row has two frees degree, so dual planetary gear planet
Carrier 16 and dual planetary gear planet row sun gear 12 are ranked without definite rotating speed；Distributed in torque in left planet row, torque distribution is left
Planet row sun gear 17 and torque distribution left lateral star seniority among brothers and sisters carrier 19 respectively with dual planetary gear planet row sun gear 12 and double-planet
Wheel planet row planet carrier 16 is structure as a whole, so torque distributes left planet row sun gear 17 and dual planetary gear planet row sun gear
12 are rotated with same rotational speed, and torque distribution left lateral star seniority among brothers and sisters carrier 19 is revolved with dual planetary gear planet row planet carrier 16 with same rotational speed
Turn, torque distribution left lateral star toothrow circle 20 has identical gear structure parameter with dual planetary gear planet row gear ring 15, so turning
Square distribution left lateral star toothrow 20 rotating speeds of circle are identical with 15 rotating speed size of dual planetary gear planet row gear ring, and direction is opposite；Due to torque
Distribution right lateral star toothrow circle 24 is structure as a whole with torque distribution left lateral star toothrow circle 20, so torque distributes right lateral star toothrow circle
24 is identical with torque distribution left lateral star toothrow 20 rotating speeds of circle, torque distribution right lateral star seniority among brothers and sisters carrier 23 and right axle shaft 8 and differential mechanism
5 rotating speed of shell is identical, and torque, which distributes right planet row sun gear 21, has definite rotating speed；At this time, motor is exported without torque, reduction planetary
Toothrow circle 28 is fixed on Driving axle housing, and reduction planetary row has two frees degree, and the rotating speed of reduction planetary row's sun gear 25 takes
Carrier 27 certainly is ranked in reduction planetary, so reduction planetary ranks carrier 27 and distributes right planet row sun gear 21 with torque with identical
Rotational speed, reduction planetary row's sun gear 25 and the rotor of motor 2 dally around X-axis.
2nd, torque allocation model
Refering to Fig. 1, figure, 3, Fig. 5, engagement torque distribution clutch 29 and separation power clutch 30, electric machine controller control
Motor work processed, motor are in motoring condition, realize torque allocation model.
Refering to Fig. 1, Fig. 3, Fig. 5, automobile is on bad road surface in tempo turn or single wheel, outboard wheels or in well
Wheel on road surface needs the torque of higher to export, and the motor work of electric machine controller control at this time, is in electric differential mechanism and turns
Square allocation model, by partial torque fixed direction allocation to the semiaxis needed, to realize the function of torque fixed direction allocation.For example, setting
The direction of rotation of wheel is positive direction during Automobile drive, otherwise is opposite direction.When automobile is in left-hand bend state, automobile right axle shaft
8 should export the torque than 7 bigger of left half axle, be travelled in favor of the left-hand bend of automobile.At this time, electric machine controller control motor 2
Rotate forward, motor output power torque, acted on by the deceleration torque of reduction planetary row, right planet row sun gear 21 is distributed in torque
Forward torque is inputted, which ranks through over torque distribution right lateral star row's amplification in torque distribution right lateral star
Carrier 23 exports forward torque and exports opposing torque in torque distribution right lateral star toothrow circle, and right lateral star rows of planetary is distributed in torque
The forward torque that frame 23 exports is output on right axle shaft 8 as fixed direction allocation torque.Torque distributes right lateral star toothrow circle 24 and turns
Square distribution left lateral star toothrow circle 20 is of the same size structural parameters, and torque distributes right planet row sun gear 21 and torque distribution
Right planet row sun gear 17 is of the same size structural parameters, and torque distribution left lateral star seniority among brothers and sisters carrier 19 output is distributed with torque
Right lateral star seniority among brothers and sisters 23 size of carrier is identical, the opposite torque in direction, so dual planetary gear planet row planet carrier 16 inputs and torque
Distribution right lateral star seniority among brothers and sisters 23 size of carrier is identical, and the opposite torque in direction, the opposing torque acts on dual planetary gear planet toothrow
Circle 15 on, give differential carrier the 5 reverse moment of resistance, at this time the output torque of differential carrier 5 for driven wheel of differential 4 input torque with
The algebraic step of the reverse moment of resistance, according to the principle of differential mechanism torque mean allocation, the output torque of differential carrier 5 will approximately be put down
Left half axle 7 and right axle shaft 8 are distributed to, right axle shaft 8 is bigger than the output torque of left half axle 7 at this time, and torque algebraic step is torque
Right lateral star seniority among brothers and sisters 23 output torque of carrier is distributed, so as to fulfill the fixed direction allocation function of torque.When automobile is in right-hand bend state,
Electric machine controller controls motor reversal, and motion principle is same as described above.Similar, it is in ice and snow or miriness in automobile single wheel
During road surface, differential mechanism is switched to torque allocation model, electric machine controller control motor output torque, by torque fixed direction allocation to another
Side is in the wheel on good road surface, ensures that automobile being capable of normally travel.
3rd, dynamic mode
Refering to Fig. 1, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Figure 10, separation torque distribution clutch 29 and engagement power clutch 30,
Realize dynamic mode, dynamic mode can control motor control according to pavement conditions, vehicle dynamic property demand and operator demand
Device processed, can be divided into electric-only mode, pattern is operated alone in engine, combines drive pattern and regeneration by electric machine operation state
Braking mode.
Electric-only mode
Refering to Fig. 1, Fig. 6, Fig. 7, under electric-only mode, torque distribution clutch 29 is in discrete state, power clutch
In engagement state.If automobile is run at a low speed on good straight road surface, and, engine stop of less demanding to dynamic property
Work, motor 2 are in motoring condition, and electric machine controller control motor 2 exports forward drive torque, arranges and slow down by reduction planetary
After torque, act on differential carrier 5, by bevel planet gear 11 and left half axle bevel gear 9, right axle shaft bevel gear 10, finally
Outputed power by left half axle 7 and right axle shaft 8, differential mechanism keeps original differential function at this time.
Pattern is operated alone in engine
Refering to Fig. 1, Fig. 6, Fig. 8, engine is operated alone under pattern, and torque distribution clutch 29 is in discrete state, moves
Power clutch is in engagement state.If running car is on good straight road surface, and battery capacity deficiency, engine are independent
Work, electric machine controller control motor 2 are in generating state, and engine power is delivered on differential carrier 5 by transmission system,
Partial power passes to rotor by reduction planetary row, charges the battery by the power generation effect of motor 2；Remaining power passes through
Bevel planet gear 11 and left half axle bevel gear 9, right axle shaft bevel gear 10 are crossed, it is finally by left half axle 7 and right axle shaft 8 that power is defeated
Go out.
Joint drive pattern
Refering to Fig. 1, Fig. 6, Fig. 9, combine under drive pattern, torque distribution clutch 29 is in discrete state, dynamic clutch
Device is in engagement state.If running car is on good straight road surface, and dynamic property requires height, such as climbing operating mode or urgency
Under accelerating mode, engine work output power, is delivered on differential carrier 5 by transmission system；Electric machine controller control electricity
Machine 2 is in motoring condition, and motor 2 exports forward torque, after reduction planetary row's deceleration torque effect, acts on differential carrier
On 5；Engine exports power with motor 2 and is coupled at differential carrier 5, by bevel planet gear 11 and left half axle bevel gear 9, the right side
Semi-axle bevel gear 10, is finally outputed power by left half axle 7 and right axle shaft 8.
Braking mode
Refering to Fig. 1, Fig. 6, Figure 10, under braking mode, torque distribution clutch 29 is in discrete state, dynamic clutch
Device is in engagement state, and electric machine controller control motor 2 is in generating state.If automobile be in non-emergent braking situation,
When the demand torque of speed higher than a certain limit value and at this time is less than the maximum braking torque that motor 2 can be provided, brake force
All provided by motor 2, mechanical energy is changed into electric energy, and be stored in battery；If automobile is in non-emergent braking
Situation, speed be more than the maximum braking torque that motor 2 can be provided higher than a certain limit value and demand torque at this time
When, the part in brake force is provided by motor 2, and mechanical energy is changed into electric energy, and is stored in battery, in brake force
Another part provided by traditional mechanical braking.
Claims (8)
1. a kind of planetary electric differential mechanism of double clutch, including main differential mechanism, it is characterised in that the double clutch planet
Formula electric differential mechanism further includes dual planetary gear planet row, torque distributes left planet row, torque distributes right planet row, reduction planetary
Row, power clutch, torque distribution clutch and motor；
The dual planetary gear planet row is sleeved on the left end of right axle shaft (8), and torque distributes left planet row and is sleeved on dual planetary gear
It is rotation connection on right axle shaft (8) on the right side of planet row, torque distributes right planet row and is sleeved on right axle shaft (8), torque distribution
Right lateral star seniority among brothers and sisters carrier (23) is connected with right axle shaft (8) for spline pair, and reduction planetary arranges the right end for being sleeved on right axle shaft (8)；It is dynamic
The active part of power clutch (30) is structure as a whole with reduction planetary seniority among brothers and sisters carrier (27), the follower of power clutch (30)
Divide the right end for being fixed on differential carrier (5), rotated jointly with differential carrier (5)；The active part of torque distribution clutch (29)
It is structure as a whole with reduction planetary seniority among brothers and sisters carrier (27), the secondary part of torque distribution clutch (29) is fixed on the torque distribution right side
The right end of planet row sun gear (21), distributes right planet row sun gear (21) with torque and rotates jointly；The housing of motor (2) is fixed
On Driving axle housing, the rotor of motor (2) is sleeved on the right end of right axle shaft (8), is one with reduction planetary row's sun gear (25)
Body structure；Main differential mechanism includes differential carrier (5), the left half axle (7) and right axle shaft (8) that can rotate about the axis, left half axle (7) and
Right axle shaft (8) can be rotated with identical or different rotating speed.
A kind of 2. planetary electric differential mechanism of double clutch described in accordance with the claim 1, it is characterised in that the left half axle
(7), right axle shaft (8), dual planetary gear planet row, torque distribute left planet row, the right planet row of torque distribution, reduction planetary and arrange, is dynamic
The rotation conllinear of power clutch (30), torque distribution clutch (29) and motor (2).
A kind of 3. planetary electric differential mechanism of double clutch described in accordance with the claim 1, it is characterised in that the power from
Clutch (30) includes active part and secondary part, by engaging the active part and secondary part of power clutch (30),
So as to fulfill the conversion of dynamic mode；Different according to the input form of power, dynamic mode is divided into electric-only mode, engine
Pattern, joint drive pattern and braking mode is operated alone.
A kind of 4. planetary electric differential mechanism of double clutch described in accordance with the claim 1, it is characterised in that the torque point
Include active part and secondary part with clutch (29), by engagement torque distribute clutch (29) active part with from
Dynamic part, so as to fulfill the conversion of torque allocation model.
A kind of 5. planetary electric differential mechanism of double clutch described in accordance with the claim 1, it is characterised in that the double-planet
Taking turns planet row includes dual planetary gear planet row sun gear (12), the first planetary gear of dual planetary gear planet row (13), dual planetary gear row
Star ranked second planetary gear (14), dual planetary gear planet row gear ring (15), dual planetary gear planet row planet carrier (16)；The duplicate rows
Star-wheel planet row sun gear (12), the first planetary gear of dual planetary gear planet row (13), the second planetary gear of dual planetary gear planet row
(14), dual planetary gear planet row gear ring (15) engages successively, dual planetary gear planet row planet carrier (16) respectively with dual planetary gear row
Star ranked first planetary gear (13) and the second planetary gear of dual planetary gear planet row (14) as rotation connection；The dual planetary gear planet
Toothrow circle (15) is structure as a whole with differential carrier (5).
A kind of 6. planetary electric differential mechanism of double clutch described in accordance with the claim 1, it is characterised in that the torque point
Include torque with left planet row and distribute left planet row sun gear (17), torque distribution left lateral star seniority among brothers and sisters star-wheel (18), torque distribution
Left lateral star seniority among brothers and sisters carrier (19), torque distribution left lateral star toothrow circle (20)；The torque distribute left planet row sun gear (17),
Torque distribution left lateral star seniority among brothers and sisters star-wheel (18), torque distribution left lateral star toothrow circle (20) engage successively, and torque distributes left planet row
Planet carrier (19) is rotation connection with torque distribution left lateral star seniority among brothers and sisters star-wheel (18)；The torque distribution left lateral star seniority among brothers and sisters carrier
(19) it is structure as a whole with dual planetary gear planet row planet carrier (16), torque distributes left planet row sun gear (17) and dual planetary gear
Planet row sun gear (12) is structure as a whole.
A kind of 7. planetary electric differential mechanism of double clutch described in accordance with the claim 1, it is characterised in that the torque point
Include torque with right planet row and distribute right planet row sun gear (21), torque distribution right lateral star seniority among brothers and sisters star-wheel (22), torque distribution
Right lateral star seniority among brothers and sisters carrier (23), torque distribution right lateral star toothrow circle (24)；The torque distribute right planet row sun gear (21),
Torque distribution right lateral star seniority among brothers and sisters star-wheel (22), torque distribution right lateral star toothrow circle (24) engage successively, and torque distributes right planet row
Planet carrier (23) is rotation connection with torque distribution right lateral star seniority among brothers and sisters star-wheel (22)；The torque distribution right lateral star toothrow circle
(24) it is structure as a whole with torque distribution left lateral star toothrow circle (20).
A kind of 8. planetary electric differential mechanism of double clutch described in accordance with the claim 1, it is characterised in that the deceleration row
Star row includes reduction planetary row's sun gear (25), reduction planetary seniority among brothers and sisters star-wheel (26), reduction planetary seniority among brothers and sisters carrier (27), deceleration row
Star toothrow circle (28)；The reduction planetary arranges sun gear (25), reduction planetary seniority among brothers and sisters star-wheel (26), reduction planetary toothrow circle
(28) engage successively, reduction planetary seniority among brothers and sisters carrier (27) is rotation connection with reduction planetary seniority among brothers and sisters star-wheel (26)；The deceleration
Planet row gear ring (28) is fixed on Driving axle housing.
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| CN201610880478.7A CN106195193B (en) | 2016-10-09 | 2016-10-09 | A kind of planetary electric differential mechanism of double clutch |
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| CN201610880478.7A CN106195193B (en) | 2016-10-09 | 2016-10-09 | A kind of planetary electric differential mechanism of double clutch |
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| CN106195193B true CN106195193B (en) | 2018-04-13 |
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| EP4088961A1 (en) * | 2021-05-12 | 2022-11-16 | Transmisiones Y Equipos Mecánicos, S.A. de C.V. | Drive system for variable distribution of torque to wheels of a vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108189665A (en) * | 2018-02-11 | 2018-06-22 | 浙江华亦海汽车电子科技有限公司 | A kind of drive system of electric automobile configuration |
| CN110030356B (en) * | 2019-04-23 | 2020-08-21 | 合肥工业大学 | Three-gear electric automobile automatic transmission based on bevel gear |
| CN113217600B (en) * | 2021-06-01 | 2022-05-06 | 吉林大学 | Automobile differential with torque vector distribution function |
| CN114083891B (en) * | 2021-11-01 | 2024-02-20 | 苏州印丝特数码科技有限公司 | Printing mechanism of double-sided printing machine |
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| JP3103779B2 (en) * | 1996-11-22 | 2000-10-30 | 建治 三村 | Differential device |
| US8663051B2 (en) * | 2010-07-14 | 2014-03-04 | E-Aam Driveline Systems Ab | Axle assembly with torque distribution drive mechanism |
| CN104675951B (en) * | 2015-02-11 | 2017-02-01 | 吉林大学 | Electric differential with double-row planetary gear torque directional distribution mechanism |
| CN205479218U (en) * | 2016-01-22 | 2016-08-17 | 吉林大学 | Electric drive device based on two keep off derailleur |
| US20160178040A1 (en) * | 2016-03-02 | 2016-06-23 | Caterpillar Inc. | Drive assembly for machines |
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| EP4088961A1 (en) * | 2021-05-12 | 2022-11-16 | Transmisiones Y Equipos Mecánicos, S.A. de C.V. | Drive system for variable distribution of torque to wheels of a vehicle |
| WO2022238475A1 (en) * | 2021-05-12 | 2022-11-17 | Transmisiones Y Equipos Mecánicos, S.A. De C.V. | Drive system for variable distribution of torque to wheels of a vehicle |
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