CN104859424B - Hydraulic auxiliary drive system by adopting wheel hub motors - Google Patents
Hydraulic auxiliary drive system by adopting wheel hub motors Download PDFInfo
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- CN104859424B CN104859424B CN201510264263.8A CN201510264263A CN104859424B CN 104859424 B CN104859424 B CN 104859424B CN 201510264263 A CN201510264263 A CN 201510264263A CN 104859424 B CN104859424 B CN 104859424B
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Abstract
The invention provides a hydraulic auxiliary drive system by adopting wheel hub motors and solves the problems that a traditional rear drive vehicle cannot meet power performance requirements on low-adhesion coefficient road surfaces and large-slope road surfaces, and the existing wheel hub motor hydraulic drive system cannot meet the requirement for high flow of wheel hub motors. The system comprises a hydraulic pump assembly, a control valve bank, a controller, a power take-off device, a power take-off device output shaft, a left front wheel, a left wheel hub motor, a right wheel hub motor, a right front wheel and a fuel tank. Reversing valves in the control valve bank are connected through a pipeline; the reversing valves in the control valve bank are connected with the controller through an electric circuit. According to the invention, a hydraulic pump is driven by the power take-off device, the working positions of the control valve bank are switched by the controller, thus multiple work modes are formed, and control fuel of hydraulically operated reversing valves is controlled by solenoid reversing valves, to control the work states of the wheel hub motors. Reliable work of the system can be guaranteed through the control valve bank, so that the requirement for the high flow of the wheel hub motors is met.
Description
Technical field
The present invention relates to a kind of hydraulic auxiliary driving system, it more particularly relates to one kind adopts hydraulic hub
Motor carries out the hydraulic system of front-wheel process auxiliary drive.
Background technology
Heavy truck and engineering truck often operation on the low attachment coefficient road surfaces such as sand ground, miriness and ice and snow, it is to power
Property require very high.For improving the dynamic property of vehicle, conventional heavy-duty vehicle is frequently with a11wheel drive, but system structure is complicated, and matter
Amount is big.At present, have and all-wheel powered scheme is proposed based on hybrid power automobile power system structure.As China Patent Publication No. is
CN101096180A, the day for announcing is 2008-01-02, discloses a kind of four-wheel driven hybrid power system, that is, adopt power to distribute
The technology of four-wheel drive realized by system, front driving axle, rear driving axle, electromotor and motor.However, present battery power density
The shortcomings of little, short life, leads to it to be unsuitable for the realization of heavy truck.
In the U.S., the country such as Japanese and French, just propose hydraulic auxiliary driving system early in 70th century, using hydraulic pressure
Pump obtains power drive hydraulic motor from electromotor, carries out process auxiliary drive to vehicle.This system has that structure is simple, specific power
Greatly, reequip the low clear superiority of cost, be preferably used for commercial heavy vehicle, and be successfully applied to many moneys vehicle.As French ripple gram
Blue company limited proposes wheel hub hydraulic pressure auxiliary front axle driving system and wheel hub hydraulic pressure auxiliary rear bridge driven system in succession, and certainly
Unload and tractor on be applied.Bosch also successfully have developed a set of fluid power traction aid system.Although it is above-mentioned each
The technology that system adopts is variant, but operation principle is similar, all includes hydraulic pump, hydraulic motor, controller in system
And the structure such as hydraulic control valve group.Wherein the most key part is exactly hydraulic control valve group, and system needs cutting in valve group
Change and realize different mode of operations, such as freewheel pattern, process auxiliary drive pattern and bypass mode etc..Currently, domestic also gradually
Carry out the research to hydraulic auxiliary driving system.If Chinese patent publication No. is CN102358163A, date of publication is 2012-
02-22, discloses a kind of hub hydraulic motor driving system, is changed into rear-guard vehicle by a set of hydraulic auxiliary driving system
The technology of 4 wheel driven configuration.But the structure of valve group is not discussed in detail in this patent.Chinese patent publication No. is CN103790876A,
Date of publication is 2114-05-14, discloses a kind of Closed circuit hydraulic transmission system, realizes system using one group of hydraulic valve different
The technology of mode of operation.Pass through the mode of operation of solenoid valve control hub motor in this patent, but the flow of electromagnetic valve is general
Less it is impossible to meet traffic requirement in practice.
Content of the invention
The present invention is to solve traditional rear-guard vehicle to meet dynamic property on low attachment coefficient road surface and heavy grade road surface
Require, existing hub hydraulic motor driving system cannot meet the problem that the big flow of hub motor requires it is proposed that one kind
Hydraulic hub motor assistant drive system, the present invention adopts the following technical scheme that realization：
Hydraulic hub motor assistant drive system, including hydraulic pump module, control valve group, controller, power takeoff, power taking
Device output shaft, the near front wheel, left wheel hub motor, right hub motor, off-front wheel, fuel tank, power takeoff output shaft and hydraulic pressure pump group
Connect for spline pair between hydraulic pump module input shaft in part or universal joint connects, external-connected port T1, T2, T3 of control valve group
All fuel tank is connected to by pipeline, external-connected port L1, L2, L3 of hydraulic pump module are connected to fuel tank, hydraulic pump by pipeline
The external-connected port G of the external-connected port M1 of assembly and control valve group is connected by pipeline, the external-connected port M2 of hydraulic pump module and control
The external-connected port A pipeline of valve group processed connects, and the external-connected port B pipeline of the external-connected port M3 of hydraulic pump module and control valve group is even
Connect, the housing oil dump port pipe of the external-connected port D1 of control valve group and the housing oil dump port of left wheel hub motor and right hub motor
Road connects, and a hydraulic fluid port pipeline of the external-connected port D2 of control valve group and left wheel hub motor connects, the external-connected port of control valve group
Another hydraulic fluid port pipeline of D3 and left wheel hub motor connects, a hydraulic fluid port of the external-connected port D4 of control valve group and right hub motor
Pipeline connects, and another hydraulic fluid port pipeline of the external-connected port D5 of control valve group and right hub motor connects, the turning of left wheel hub motor
Be connected using spline pair between sub- axle and the power transmission shaft of the near front wheel or both be same axis, the armature spindle of right hub motor with right
Adopt spline pair to connect between the power transmission shaft of front-wheel or both are same axis, controller is with hydraulic pump module by holding wire even
Connect, controller is connected with control valve group circuit, controller and hydraulic pump module circuit connect it is characterised in that：
Control valve group includes：No. four overflow valves, No. three three position three-way change valves, two-position four way change valve, No. one two
Position three-way diverter valve, No. two two position three way directional control valves, No. two two-position four way change valves, two-position four-way hydraulic pilot commutations
Valve, No. two two-position four-way hydraulic pilot reversal valves and No. five overflow valves, wherein, No. three three position three-way change valves, No. one two four
Logical reversal valve, a two position three way directional control valve and No. two two-position four way change valves are all solenoid directional control valve, No. four overflow valves and five
Number overflow valve is direct acting type overflow valve, No. two two position three way directional control valves, a two-position four-way hydraulic pilot reversal valve and No. two two
Position four-way hydraulic pilot reversing valve is all hydraulic pilot reversal valve；
The T-port of No. three three position three-way change valves is connected with No. four overflow valve oil-in pipelines, No. four overflow valves fuel-displaced
Mouthful it is connected with the external-connected port T1 pipeline of control valve group, the P port of No. three three position three-way change valves and the external connection end of control valve group
Mouth A, the P port tube of No. two two position three way directional control valves connect, and the B port of No. three three position three-way change valves is outer with control valve group
Connect port B, the T-port of No. two two position three way directional control valves, the P port of a two-position four-way hydraulic pilot reversal valve, No. two two
The connection of T-port pipeline, the B port of No. two two position three way directional control valves and a two-position four-way hydraulic pressure of four-way hydraulic pilot reversing valve
The T-port of pilot reversing valve, the P port tube of No. two two-position four-way hydraulic pilot reversal valves connect, a two-position four-way commutation
The P port of valve and the external-connected port G of control valve group, the P port of a two position three way directional control valve, No. two two-position four way change valves
P port tube connects, the A port of the T-port of a two-position four way change valve and a two position three way directional control valve, No. two two four
The T-port of logical reversal valve, control valve group external-connected port T2 pipeline connect, the A port of a two-position four way change valve with No. two
Control port X of two-position four-way hydraulic pilot reversal valve, the oil-in of No. five overflow valves, the external-connected port D1 pipeline of control valve group
Connect, the B port of a two-position four way change valve is connected with the control port Y pipeline of No. two two-position four-way hydraulic pilot reversal valves
Connect, the T-port of a two position three way directional control valve is connected with the control port pipeline of No. two two position three way directional control valves, No. two two four
The A port of logical reversal valve is connected with the control port X-tube road of a two-position four-way hydraulic pilot reversal valve, and No. two two-position four-ways change
It is connected to the B port of valve with the control port Y pipeline of a two-position four-way hydraulic pilot reversal valve, a two-position four-way hydraulic pressure is first
The external-connected port D5 pipeline of the B port and control valve group of leading reversal valve is connected, the A end of a two-position four-way hydraulic pilot reversal valve
Mouthful it is connected with the external-connected port D4 pipeline of control valve group, the A port of No. two two-position four-way hydraulic pilot reversal valves and control valve group
External-connected port D2 pipeline connect, the B port of No. two two-position four-way hydraulic pilot reversal valves and the external-connected port D3 of control valve group
Pipeline connects, and the oil-out of No. five overflow valves is connected with the external-connected port T3 pipeline of control valve group.
Further technical scheme includes：
Described controller and the connection of control valve group circuit refer to：
The input of the solenoid at No. three three position three-way change valve two ends in control valve group is connected by electric wire respectively
To the port LA05 of the controller and port LA06 of controller；
The input of the solenoid of a two-position four way change valve in control valve group is connected by electrical wiring to controller
Port LA07；
The input of the solenoid of a two position three way directional control valve in control valve group is connected by electrical wiring to controller
Port LA24；
The input of the solenoid of No. two two-position four way change valves in control valve group is connected by electrical wiring to controller
Port LA25.
Described controller and the connection of hydraulic pump module circuit refer to：
A three position three-way change valve in hydraulic pump module is solenoid directional control valve, the solenoid in its two ends electric magnet
Input be connected by electrical wiring to the port LA00 of the controller and port LA01 of controller respectively；
No. two three position three-way change valves in hydraulic pump module are solenoid directional control valves, the solenoid in its two ends electric magnet
Input be connected by electrical wiring to the port LA02 of the controller and port LA03 of controller respectively；
One end away from hydraulic pump of hydraulic cylinder in hydraulic pump module is provided with displacement transducer, displacement transducer defeated
Go out signal to connect by holding wire to the port EAD00 of controller；
Bi-bit bi-pass reversal valve in hydraulic pump module is solenoid directional control valve, the input of the solenoid in its electric magnet
It is connected by electrical wiring to the port LA04 of controller.
Hydraulic hub motor assistant drive system obtains power drive hydraulic pump by power takeoff from electromotor, by control
The operating position of device switching control valve group processed, thus forming multiple-working mode, such as freewheel pattern, process auxiliary drive pattern and side
Logical pattern, controls the control fluid of hydraulicchange-over valve by solenoid directional control valve, thus controlling the working condition of hub motor, can
The big flow meeting hub motor requires.
Compared with prior art, the invention has the beneficial effects as follows：
1. vehicle front-wheel can be changed into driving by hydraulic hub motor assistant drive system proposed by the present invention from non-driving wheel
Driving wheel, is conducive to improving the dynamic property of vehicle.
2. in hydraulic hub motor assistant drive system proposed by the present invention, hydraulic pump module is integrated with main pump and regulation
The structures such as the servo-control mechanism of its discharge capacity, oil-supplementing system and overflow valve, hydraulic motor adopt radial plunger type motor, and by its
It is integrated in the wheel hub of front-wheel, whole system physical dimension is little, takes up room little, arrangement is simple and convenient with installation；
3. the control valve group in hydraulic hub motor assistant drive system proposed by the present invention disclosure satisfy that in Practical Project
The big flow of hub motor requires, it is possible to achieve hub motor switches under different conditions, has preferable adaptability for working condition；
4. in hydraulic hub motor assistant drive system proposed by the present invention, when hub motor is in freewheel state,
Hydraulic control valve group can make to retain certain pressure in motor shell, so that motor piston and motor shell is completely separated it is ensured that
Additional load will not be applied to front-wheel when motor does not work；
5. in hydraulic hub motor assistant drive system proposed by the present invention, when vehicle is shifted gears, by control valve
Hub motor is bypassed by group, and gearshift is rapid after terminating to recover driving condition, which decreases hydraulic motor short time switching state
The pressure change of Shi Mada working connection, reduces the compression shock of motor shell, improves the working life of hydraulic motor；
6., in hydraulic hub motor assistant drive system of the present invention, Hydraulic Elements each in control valve group are collected
Cheng Hua, reduces the volume shared by hydraulic system.
Brief description
The present invention is further illustrated below in conjunction with the accompanying drawings：
Fig. 1 is a kind of structure principle chart of hydraulic hub motor assistant drive system of the present invention；
Fig. 2 is hydraulic hub motor assistant drive system control valve group structure chart of the present invention；
Fig. 3 is hydraulic hub motor assistant drive system of the present invention each reversal valve work under freewheel pattern
Make position view；
Fig. 4 is hydraulic hub motor assistant drive system of the present invention each reversal valve under process auxiliary drive pattern
Operating position schematic diagram；
Fig. 5 is each reversal valve work under bypass mode for the hydraulic hub motor assistant drive system of the present invention
Position view；
Fig. 6 is by simulating, verifying, and obtained hydraulic hub motor assistant drive system of the present invention is to raising
The pull strength of car load and climbable gradient increase ratio chart.
In figure：1. power takeoff, 2. power takeoff output shaft, 3. hydraulic pump module input shaft, 4. a 3-position-3-way change
To valve, 5. No. two three position three-way change valves, 6. hydraulic cylinder, 7. hydraulic pump, 8. slippage pump, a 9. overflow valve, 10. bi-bit bi-pass
Reversal valve, No. 11. check valves, 12. No. two overflow valves, 13. No. two check valves, 14. No. three overflow valves, 15. No. three check valves,
16. No. four overflow valves, 17. No. three three position three-way change valves, No. 18. two-position four way change valves, No. 19. two-position three way commutations
Valve, 20. No. two two position three way directional control valves, 21. No. two two-position four way change valves, No. 22. two-position four-way hydraulic pilot reversal valves,
23. No. two two-position four-way hydraulic pilot reversal valves, 24. No. five overflow valves, 25. the near front wheels, 26. left wheel hub motors, 27. right wheel hubs
Motor, 28. off-front wheels, 29. fuel tanks, 30. controllers, S. displacement transducer, I. hydraulic pump module, II. control valve group.
M1, M2, M3, L1, L2, L3 be hydraulic pump module I external-connected port, G, A, B, T1, T2, T3, D1, D2, D3, D4,
D5 is the external-connected port of control valve group II.
Specific embodiment
Below in conjunction with the accompanying drawings the present invention is described in detail.
Refering to accompanying drawing 1, hydraulic hub motor assistant drive system proposed by the present invention includes hydraulic pump module I, control valve
Group II, controller 30 and power takeoff 1, power takeoff output shaft 2, the near front wheel 25, left wheel hub motor 26, right hub motor
27th, off-front wheel 28, fuel tank 29.
Refering to accompanying drawing 1, power takeoff 1 and power takeoff output shaft 2 provide power for hydraulic pump module I, and power takeoff is defeated
Connect for mechanical type between shaft 2 and hydraulic pump module input shaft 3, connected mode can be common key or spline pair or pass through ten thousand
Connect to section, the effect of power takeoff 1 and power takeoff output shaft 2 is to impart power to hydraulic pump module I, so that hydraulic pressure
Pump group part I exports steady fluid.
Refering to accompanying drawing 1, hydraulic pump module I includes：Hydraulic pump module input shaft 3, a three position three-way change valve 4, No. two
Three position three-way change valve 5, hydraulic cylinder 6, hydraulic pump 7, slippage pump 8, an overflow valve 9, bi-bit bi-pass reversal valve 10, No. one is unidirectional
Valve 11, No. two overflow valves 12, No. two check valves 13, No. three overflow valves 14, No. three check valves 15.Wherein, hydraulic cylinder 6 is double-piston
Bar hydraulic cylinder；Hydraulic pump 7 is axial piston bidirectional variable hydraulic pump；Slippage pump 8 is unidirectional quantitative gear pump；No. one three three
Logical reversal valve 4 and No. two three position three-way change valves 5 are all solenoid directional control valves；9, No. two overflow valves 12 of a number overflow valve and No. three
Overflow valve 14 is all direct acting type overflow valve；11, No. two check valves 13 of a number check valve and No. three check valves 15 are Direct Action Type list
To valve.
Refering to accompanying drawing 1, hydraulic pump module input shaft 3 is same axis with the armature spindle of hydraulic pump 7, slippage pump 8；No. one three
The T-port of the T-port of position three-way diverter valve 4 and No. two three position three-way change valves 5, the external-connected port L1 pipeline of hydraulic pump module I
Connection, the P port of a three position three-way change valve 4 and the P port of No. two three position three-way change valves 5, slippage pump 8 oil-out pipeline
Connect, the A port of a three position three-way change valve 4 is connected with a hydraulic fluid port pipeline of hydraulic cylinder 6, another oil of hydraulic cylinder 6
Mouth is connected with the A port tube of No. two three position three-way change valves 5, and one end of hydraulic cylinder 6 piston rod is adopted with the swash plate of hydraulic pump 7
Ball pivot connects, and the oil-in of the oil-out of slippage pump 8 and an overflow valve 9, the P port tube of bi-bit bi-pass reversal valve 10 connect
Connect, the A port of bi-bit bi-pass reversal valve 10 and check valve 11 oil-in, No. two overflow valve 12 oil-outs, No. two check valves
13 oil-ins, No. three overflow valve 14 oil-outs, No. three check valve 15 oil-in pipelines connections, No. three check valve 15 oil-outs and liquid
The connection of external-connected port M1 pipeline, a hydraulic fluid port of hydraulic pump 7 and check valve 11 oil-out, No. two overflows of press pump assembly I
Valve 12 oil-in, the connection of external-connected port M2 pipeline, another hydraulic fluid port of hydraulic pump 7 and No. two check valves 13 of hydraulic pump module I
Oil-out, No. three overflow valve 14 oil-ins, the connection of external-connected port M3 pipelines, the oil-in of slippage pump 8 and the liquid of hydraulic pump module I
The external-connected port L2 pipeline of press pump assembly I connects, the external-connected port L3 pipe of the oil-out of an overflow valve 9 and hydraulic pump module I
Road connects.
Refering to accompanying drawing 2, control valve group II includes：No. four overflow valves 16, No. three three position three-way change valves 17, No. one two four
Logical reversal valve 18, a two position three way directional control valve 19, No. two two position three way directional control valves 20, No. two two-position four way change valves 21, one
Number two-position four-way hydraulic pilot reversal valve 22, No. two two-position four-way hydraulic pilot reversal valves 23, No. five overflow valves 24.Wherein, three
Number three position three-way change valve 18, two position three way directional control valve 19 of 17, two-position four way change valve and No. two two-position four-ways change
It is all solenoid directional control valve to valve 21；No. four overflow valves 16 and No. five overflow valves 24 are direct acting type overflow valves；No. two two-position three ways change
It is all hydraulic pilot to 20, two-position four-way hydraulic pilot reversal valve 22 of valve and No. two two-position four-way hydraulic pilot reversal valves 23
Reversal valve.
Refering to accompanying drawing 2, the T-port of No. three three position three-way change valves 17 is connected with No. four overflow valves 16 oil-in pipeline, and four
Number overflow valve 16 oil-out is connected with the external-connected port T1 pipeline of control valve group II, the P port of No. three three position three-way change valves 17
It is connected with the external-connected port A of control valve group II, the P port tube of No. two two position three way directional control valves 20, No. three 3-position-3-way commutations
The B port of valve 17 and the external-connected port B of control valve group II, the T-port of No. two two position three way directional control valves 20, a two-position four-way liquid
The P port of pressure pilot reversing valve 22, the T-port pipeline of No. two two-position four-way hydraulic pilot reversal valves 23 connect, No. two two three
The B port of logical reversal valve 20 is changed with the T-port of a two-position four-way hydraulic pilot reversal valve 22, No. two two-position four-way hydraulic pilots
Connect to the P port tube of valve 23, the P port of a two-position four way change valve 18 and the external-connected port G of control valve group II, No. one
The P port of two position three way directional control valve 19, the P port tube of No. two two-position four way change valves 21 connect, a two-position four-way commutation
The A port of the T-port of valve 18 and a two position three way directional control valve 19, the T-port of No. two two-position four way change valves 21, control valve group
II external-connected port T2 pipeline connects, and is commutated with No. two two-position four-way hydraulic pilots in the A port of a two-position four way change valve 18
Control port X of valve 23, No. five overflow valve 24 oil-ins, the external-connected port D1 pipelines of control valve group II connect, No. one two four
The B port of logical reversal valve 18 is connected with the control port Y pipeline of No. two two-position four-way hydraulic pilot reversal valves 23, No. one two three
The T-port of logical reversal valve 19 is connected with the control port pipeline of No. two two position three way directional control valves 20, No. two two-position four way change valves
21 A port is connected with the control port X-tube road of a two-position four-way hydraulic pilot reversal valve 22, No. two two-position four way change valves
21 B port is connected with the control port Y pipeline of a two-position four-way hydraulic pilot reversal valve 22, and a two-position four-way hydraulic pressure is first
The external-connected port D5 pipeline of the B port and control valve group II of leading reversal valve 22 is connected, a two-position four-way hydraulic pilot reversal valve
22 A port is connected with the external-connected port D4 pipeline of control valve group II, the A port of No. two two-position four-way hydraulic pilot reversal valves 23
It is connected with the external-connected port D2 pipeline of control valve group II, the B port of No. two two-position four-way hydraulic pilot reversal valves 23 and control valve
The external-connected port D3 pipeline of group II connects, and No. five overflow valve 24 oil-outs are connected with the external-connected port T3 pipeline of control valve group II.
Refering to accompanying drawing 3, controller 30 existing procucts, depending on concrete type selecting can be by practical situation, control type as used herein
Number be HY-TTC200-CD-538K-2.4M-WD00-000.Controller 30 is used for receiving the output signal of displacement transducer s, with
When control 4, No. two three position three-way change valves 5 of a three position three-way change valve, 10, No. three 3-position-3-ways of bi-bit bi-pass reversal valve to change
Working position to 17, two-position four way change valve of valve, 19, No. two two-position four way change valves 21 of 18, two position three way directional control valve
Put.
Refering to accompanying drawing 3, a three position three-way change valve 4 is solenoid directional control valve, and electric magnet manipulates, spring reset, its two ends
The input of the solenoid in electric magnet is connected by electrical wiring to the port LA00 of controller 30 and the end of controller 30 respectively
Mouth LA01；No. two three position three-way change valves 5 are solenoid directional control valves, and the input of the solenoid in its two ends electric magnet leads to respectively
Cross the port LA03 of the port LA02 being wired to controller 30 and controller 30；Hydraulic cylinder 6 another away from hydraulic pump 7
End is provided with displacement transducer s, and the cylinder body of hydraulic cylinder is mechanically fixed on the housing of hydraulic pump module I, and displacement passes
The output signal of sensor s is by being wired to the port EAD00 of controller 30；Bi-bit bi-pass reversal valve 10 is electromagnetic switch
Valve, the input of the solenoid in its electric magnet is connected by electrical wiring to the port LA04 of controller 30；No. three 3-position-3-ways
Reversal valve 18, two position three way directional control valve 19 of 17, two-position four way change valve and No. two two-position four way change valves 21 are all
It is solenoid directional control valve；The input of the solenoid at No. three three position three-way change valve 17 two ends is connected by electrical wiring to control respectively
The port LA05 of the device 30 and port LA06 of controller 30；The input of the solenoid of a number two-position four way change valve 18 passes through
It is wired to the port LA07 of controller 30；The input of the solenoid of a number two position three way directional control valve 19 is by electric wire even
It is connected to the port LA24 of controller 30；The input of the solenoid of No. two two-position four way change valves 21 is connected by electrical wiring to control
The port LA25 of device 30 processed.
Refering to accompanying drawing 3, external-connected port T1, T2, T3 of control valve group II are connected to fuel tank 29 by pipeline；Hydraulic pressure pump group
External-connected port L1, L2, L3 of part I are connected to fuel tank 29 by pipeline；The external-connected port M1 of hydraulic pump module I and control valve group
II external-connected port G pipeline connects, and the external-connected port A pipeline of the external-connected port M2 of hydraulic pump module I and control valve group II connects,
The external-connected port B pipeline of the external-connected port M3 of hydraulic pump module I and control valve group II connects.
Refering to accompanying drawing 3, the external-connected port D1 of control valve group II and the housing oil dump port of left wheel hub motor 26, right wheel hub horse
Reach 27 housing oil dump port pipeline connection；The external-connected port D2 of control valve group II and a hydraulic fluid port pipeline of left wheel hub motor 26
Connect；Another hydraulic fluid port pipeline of the external-connected port D3 of control valve group II and left wheel hub motor 26 connects；Outside control valve group II
Meet port D4 and a hydraulic fluid port pipeline of right hub motor 27 connects；The external-connected port D5 of control valve group II and right hub motor 27
Another hydraulic fluid port pipeline connect；Left wheel hub motor 26 is radial plunger type two-way quantitative motor, its armature spindle and the near front wheel 25
Power transmission shaft between using spline pair connect or both be same axis；Right hub motor 27 is also radial plunger type two-way quantitative
Motor, is connected using spline pair between its armature spindle and the power transmission shaft of off-front wheel 28 or both are same axis；
Refering to accompanying drawing 3, power takeoff 1 and power takeoff output shaft 2 provide motive power for hydraulic auxiliary driving system, drive
Hydraulic pump 7 and slippage pump 8 rotate；Hydraulic pump 7 is bidirectional variable hydraulic pump, two hydraulic fluid port both can be oil-in it is also possible to
It is oil-out, but operationally only has an oil-out and an oil-in, the discharge capacity of hydraulic pump 7 passes through the piston of hydraulic cylinder 6
Bar drives swash plate aperture to adjust；The housing of hydraulic cylinder 6 is adopted and is mechanically fixed, and displacement transducer s is by the displacement of piston rod
Pass to controller 30, controller 30 obtains the feedback discharge capacity of hydraulic pump 7 by the signal value of displacement transducer s, thus formed closing
Ring controls；Slippage pump 8 is unidirectional quantitative hydraulic pump, and its effect is to system circuit repairing, provides control for control valve group II simultaneously
Liquefaction liquid；A number check valve 12, No. two check valves 13 of 11, No. two overflow valves and No. three overflow valves 14 be used for only allowing fluid from
The A port of bi-bit bi-pass reversal valve 10 flows to working connection, ensures the safety of working connection simultaneously；When bi-bit bi-pass reversal valve 10 is cut
When shifting to bottom, the output fluid of slippage pump 8 flows to the oil-feed of No. three check valves 15 through the P port of bi-bit bi-pass reversal valve 10
Mouthful, export from the external-connected port M1 of hydraulic pump module I after No. three check valves 15, thus being a two-position four-way hydraulic pilot
Reversal valve 22 and No. two two-position four-way hydraulic pilot reversal valves 23 provide and control oil, and by a two position three way directional control valve 19 are
No. two two position three way directional control valves 20 provide and control fluid (now a two position three way directional control valve 19 switches to right position).A number overflow
Valve 9 is arranged between the oil-out of slippage pump 8 and fuel tank 29, to limit the oil-out pressure of slippage pump 8, thus reach protection mending
The purpose of oil pump 8.
Refering to accompanying drawing 3, by controlling the operating position of a three position three-way change valve 4 and No. two three position three-way change valves 5
To control the piston movement of hydraulic cylinder 6, thus changing the swash plate aperture of hydraulic pump 7 to reach the purpose changing discharge capacity, No. one three
The input fluid of position three-way diverter valve 4 and No. two three position three-way change valves 5 is provided by slippage pump 8.When controller 30 output control
Order, a three position three-way change valve 4 is switched to bottom, when No. two three position three-way change valves 5 being switched to bottom simultaneously, this
When be disconnected hydraulic cylinder 6 with the oil circuit between slippage pump 8, hydraulic cylinder 6 two ends all connect with fuel tank 29, the now row of hydraulic pump 7
Measure as 0.When a three position three-way change valve 4 and No. two three position three-way change valves 5 all being switched to middle position using controller 30,
Now pressurize is carried out to the hydraulic pressure at hydraulic cylinder 6 piston two ends then it represents that keeping the discharge capacity of hydraulic pump 7 to stablize.If by No. one three
Three-way diverter valve 4 switches to upper, No. two three position three-way change valves 5 is switched to bottom, then the piston of hydraulic cylinder 6 moves down, this
When hydraulic pump 7 displacement signal value be gradually increased in 0～+1 scope.If a three position three-way change valve 4 is switched to bottom, will
No. two three position three-way change valves 5 switch to upper, now then move on the piston of hydraulic cylinder 6, and the displacement signal value of hydraulic pump 7 is -1
～0 scope is gradually increased (absolute value increase).Controller 30 is obtained by the displacement transducer s being arranged on hydraulic cylinder 6 piston rod
Obtain the displacement of hydraulic cylinder 6 piston rod, itself and desired value are compared and form closed loop control.
Refering to accompanying drawing 3, when in system, oil liquid temperature rises to certain threshold value, by controller 30 output control order, cut
Change the operating position of No. three three position three-way change valves 17, partial high pressure fluid is unloaded, by slippage pump 8, working connection is mended
Oil, thus reach the purpose of cooling.It is specially：When the vehicle is moving in a forward direction, No. three three position three-way change valves 17 are switched to
Position, when vehicle backing travels, No. three three position three-way change valves 17 is switched to bottom.
By controller 30 output control signal, make 4, No. two three position three-way change valves 5, two of a three position three-way change valve
Position 10, No. three three position three-way change valves of two way selected valve, 18, two position three way directional control valve of 17, two-position four way change valve
19th, No. two two-position four way change valves 21 are in different operating positions, and system can be made to realize three kinds of different operational modes, that is, certainly
By wheel pattern, process auxiliary drive pattern and bypass mode, it is described in detail below.
Freewheel pattern：
Refering to accompanying drawing 3, now hydraulic hub motor assistant drive system works in freewheel pattern.
By controller 30 output control order, a three position three-way change valve 4 is switched to bottom, No. two 3-position-3-ways change
Switch to bottom to valve 5, bi-bit bi-pass reversal valve 10 switches to bottom, No. three three position three-way change valves 17 switch to middle position, one
Number two-position four way change valve 18 switches to upper, and a two position three way directional control valve 19 switches to left position, No. two two-position four-ways commutations
Valve 21 switches to bottom.The external-connected port L2 that slippage pump 8 passes through hydraulic pump module I draws fluid from fuel tank 29, by two two
After logical 10, No. three check valves 15 of reversal valve, the external-connected port M1 of the hydraulic pump module I and external-connected port G of control valve group II respectively
Act on No. two two-position four-way hydraulic pilots after a two-position four way change valve 18 and No. two two-position four way change valves 21 to change
To the X end of valve 23 and the Y end of a two-position four-way hydraulic pilot reversal valve 22, by a two-position four-way hydraulic pilot reversal valve 22
Switch to bottom, No. two two-position four-way hydraulic pilot reversal valves 23 are switched to upper, lead to left wheel hub motor 26 and right wheel hub
Motor 27 is disconnected with working connection；Meanwhile, the external-connected port D1 of control valve group II is passed through in the A port of a two-position four way change valve 18
It is delivered to left wheel hub motor 26 and the housing of right hub motor 27, so that the plunger of left wheel hub motor 26 and right hub motor 27
Inside contract and separate with housing, No. five overflow valves 24 are used for pressure being limited in suitable scope, to ensure safety；Now, liquid
Cylinder pressure 6 piston two ends all connect with fuel tank 29, and the discharge capacity of hydraulic pump 7 is 0.
Process auxiliary drive pattern：
Refering to accompanying drawing 4, now hydraulic hub motor assistant drive system works in process auxiliary drive pattern.
By controller 30 output control order, bi-bit bi-pass reversal valve 10 is switched to bottom, No. three 3-position-3-way commutations
The operating position of valve 17 indefinite (according to system status, can switch to one of upper, middle position and bottom), a two-position four-way
Reversal valve 18 switches to bottom, and a two position three way directional control valve 19 switches to left position, and No. two two-position four way change valves 21 switch to
Upper；Now, No. two two position three way directional control valves 20 work in upper；In the presence of controlling fluid, a two-position four-way hydraulic pressure
Pilot reversing valve 22 switches to upper, No. two two-position four-way hydraulic pilot reversal valves 23 is switched to bottom, now left wheel hub horse
Reach 26 and right hub motor 27 be connected with working connection.Hydraulic pump 20, No. two two-position four-way hydraulic pressure of 7, No. two two position three way directional control valves
Pilot reversing valve 23 and left wheel hub motor 26 form closed loop, realize driving left wheel hub motor 26 to rotate, closely drive left front
Wheel 25 traveling；In the same manner, 20, two-position four-way hydraulic pilot reversal valve 22 of 7, No. two two position three way directional control valves of hydraulic pump and right wheel
Hub motor 27 forms loop, thus driving off-front wheel 28 to travel.Controller 30 passes through to switch a three position three-way change valve 4 and two
The displacement to control hydraulic cylinder 6 piston for the operating position of number three position three-way change valve 5, thus reach adjust hydraulic pump 7 discharge capacity
Purpose, specially：If switching to a three position three-way change valve 4 upper, No. two three position three-way change valves 5 are switched to down
Position, then hydraulic pump 7 driving left wheel hub motor 26 and right hub motor 27 Positive work, now vehicle forward travel；If by No. one
Three position three-way change valve 4 switches to bottom, No. two three position three-way change valves 5 is switched to upper, then hydraulic pump 7 drives left wheel hub
Motor 26 and right hub motor 27 antiport, now vehicle backing traveling.A number three position three-way change valve 4 and No. two three three
Depending on discharge capacity needed for hydraulic pump 7 for the operating position of logical reversal valve 5.
Bypass mode：
Refering to accompanying drawing 5, now hydraulic hub motor assistant drive system works in bypass mode.
When system works in process auxiliary drive pattern, when vehicle is shifted gears, by hydraulic hub motor assistant drive system
Switch to bypass mode, now only need to change the working position of a two position three way directional control valve 19 by the output signal of controller 30
Put, the operating position of other parts (as reversal valve, hydraulic pump, motor etc.) is constant.Because vehicle only one of which is reversed gear, in vehicle
There is not shift process in reverse travel, during switching to forward range by reversing gear, need to be cut when speed is zero
Change, so hydraulic hub motor assistant drive system does not have bypass mode when vehicle backing travels.When vehicle is to moving ahead
When sailing middle gearshift, a two position three way directional control valve 19 is switched to right position, now the T-port of a two position three way directional control valve 19 and
P port turns on, and No. two two position three way directional control valves 20 is switched to bottom, is now delivered to left wheel hub motor 26 and right hub motor
27 hydraulic oil is cut off, and hydraulic hub motor assistant drive system works in bypass mode.Number three position three-way change valve 4 He
No. two three position three-way change valves 5 are in that to switch to the position that the previous moment of bypass mode is located constant.
Element used all existing procucts in the present invention, depending on concrete type selecting need to be in conjunction with whole-car parameterses and design requirement, table 1 is
The car load basic parameter of certain heavy vehicle and design requirement, table 2 is the parameter of selected main hydraulic.
Table 1 car load basic parameter and design requirement
Table 2 main hydraulic parameter
For verifying the feasibility of hydraulic hub motor assistant drive system of the present invention, by the emulation testing present invention couple
Improve the contribution of power performance.
Refering to accompanying drawing 6, in figure shows after using hydraulic hub motor assistant drive system of the present invention, vehicle
The increase ratio of dynamic property.In figure, solid line represents that pull strength increases the change curve with coefficient of road adhesion for the ratio, and dotted line represents
Maximum climbable gradient of vehicle increases the change curve with coefficient of road adhesion for the ratio.As can be seen that when using liquid of the present invention
After hub motor assistant drive system, the max. climb slope of vehicle and pull strength are improved significantly, on low attachment coefficient road
On face, effect becomes apparent from.
Hydraulic hub motor assistant drive system of the present invention can realize freewheel pattern, process auxiliary drive pattern and
Bypass mode, in control valve group II under each mode of operation, the operating position of reversal valve is as shown in table 3 below：
The operating position of reversal valve under each mode of operation of table 3
The principle features of this hydraulic hub motor assistant drive system：
1. controller 30 is according to the mode of operation of speed, the position signalling decision systems of accelerator pedal, by switching control
In valve group II, the operating position of each reversal valve to be realizing different mode of operations, by controlling three position three-way change valve 4 He
The operating position of No. two three position three-way change valves 5 adjusting the discharge capacity of hydraulic pump 7, to meet drive demand.
2., when vehicle travels on low attachment coefficient road surface or climbing, respectively commutated by controller 30 switching control valve group II
The operating position of valve, makes system work in process auxiliary drive pattern, now vehicle front-wheel is changed into driving wheel, increased vehicle traction
Power.
3., when vehicle travels in good road surface, hydraulic hub motor assistant drive system works in freewheel pattern, this
When front-wheel be driven pulley, this is favorably improved car load propulsive efficiency.
4. when vehicle shift, hydraulic hub motor assistant drive system works in bypass mode, thus ensureing that gearshift is flat
Surely complete.
5. hydraulic hub motor assistant drive system of the present invention can produce certain heat at work unavoidably, is
Guarantee system reliably working, can reach the purpose of cooling by switching the operating position of No. three three position three-way change valves 17.
Can be seen that the present invention according to above principle features on the basis of traditional rear wheel drive vehicle, by adding one
Set hydraulic hub motor assistant drive system, vehicle refitting is become four-wheel drive system, is favorably improved car load dynamic property.Meanwhile, originally
Described control valve group II structure of invention disclosure satisfy that Practical Project requires, and can efficiently control huge discharge hydraulic hub motor
Work so as to steady output driving torque, have good adaptability for working condition.
Claims (3)
1. hydraulic hub motor assistant drive system, including hydraulic pump module (I), control valve group (II), controller (30), power taking
Device (1), power takeoff output shaft (2), the near front wheel (25), left wheel hub motor (26), right hub motor (27), off-front wheel
(28), fuel tank (29), are colored between the hydraulic pump module input shaft (3) in power takeoff output shaft (2) and hydraulic pump module (I)
Key is secondary to be connected or universal joint connection, and external-connected port T1, T2, T3 of control valve group (II) are connected to fuel tank (29) by pipeline,
External-connected port L1, L2, L3 of hydraulic pump module (I) is connected to fuel tank (29), the external connection end of hydraulic pump module (I) by pipeline
The external-connected port G of mouthful M1 and control valve group (II) is connected by pipeline, the external-connected port M2 of hydraulic pump module (I) and control valve group
(II) external-connected port A pipeline connects, the external-connected port B pipe of the external-connected port M3 of hydraulic pump module (I) and control valve group (II)
Road connection, the housing oil dump port of the external-connected port D1 of control valve group (II) and left wheel hub motor (26) and right hub motor (27)
Housing oil dump port pipeline connect, a hydraulic fluid port pipeline of the external-connected port D2 of control valve group (II) and left wheel hub motor (26)
Connect, another hydraulic fluid port pipeline of the external-connected port D3 of control valve group (II) and left wheel hub motor (26) connects, control valve group
(II) a hydraulic fluid port pipeline of external-connected port D4 and right hub motor (27) connects, the external-connected port D5 of control valve group (II) and
Another hydraulic fluid port pipeline of right hub motor (27) connects, the power transmission shaft of the armature spindle of left wheel hub motor (26) and the near front wheel (25)
Between connected using spline pair or both are same axis, the armature spindle of right hub motor (27) and the power transmission shaft of off-front wheel (28)
Between connected using spline pair or both are same axis, controller (30) is connected by holding wire with hydraulic pump module (I), controls
Device (30) processed is connected with control valve group (II) circuit, controller (30) and hydraulic pump module (I) circuit connect it is characterised in that：
Control valve group (II) includes：No. four overflow valves (16), No. three three position three-way change valves (17), two-position four way change valves
(18), two position three way directional control valve (19), No. two two position three way directional control valves (20), No. two two-position four way change valves (21), one
Number two-position four-way hydraulic pilot reversal valve (22), No. two two-position four-ways hydraulic pilot reversal valve (23) and No. five overflow valves (24),
Wherein, No. three three position three-way change valves (17), two-position four way change valve (18), two position three way directional control valves (19) and two
Number two-position four way change valve (21) is all solenoid directional control valve, and No. four overflow valves (16) and No. five overflow valves (24) are direct acting type overflows
Valve, No. two two position three way directional control valves (20), two-position four-way hydraulic pilot reversal valve (22) and No. two two-position four-way hydraulic pressure are first
Leading reversal valve (23) is all hydraulic pilot reversal valve；
The T-port of No. three three position three-way change valves (17) is connected with No. four overflow valve (16) oil-in pipelines, No. four overflow valves
(16) oil-out is connected with the external-connected port T1 pipeline of control valve group (II), the P port of No. three three position three-way change valves (17)
It is connected with the external-connected port A of control valve group (II), the P port tube of No. two two position three way directional control valves (20), No. three 3-position-3-ways
The external-connected port B of the B port of reversal valve (17) and control valve group (II), the T-port of No. two two position three way directional control valves (20), No. one
The P port of two-position four-way hydraulic pilot reversal valve (22), the T-port pipeline of No. two two-position four-ways hydraulic pilot reversal valve (23) connect
Connect, the T-port of the B port of No. two two position three way directional control valves (20) and two-position four-way hydraulic pilot reversal valve (22), No. two
The connection of P port tube, the P port of a two-position four way change valve (18) and the control of two-position four-way hydraulic pilot reversal valve (23)
The external-connected port G of valve group (II), the P port of a two position three way directional control valve (19), the P end of No. two two-position four way change valves (21)
Mouthful pipeline connects, the A port of the T-port of a two-position four way change valve (18) and a two position three way directional control valve (19), No. two
The T-port of two-position four way change valve (21), the external-connected port T2 pipeline of control valve group (II) connect, a two-position four way change valve
(18) A port and control port X of No. two two-position four-ways hydraulic pilot reversal valve (23), the oil-feed of No. five overflow valves (24)
Mouthful, the external-connected port D1 pipeline of control valve group (II) connect, the B port of a two-position four way change valve (18) with No. two two four
The control port Y pipeline of logical hydraulic pilot reversal valve (23) connects, the T-port of a two position three way directional control valve (19) and No. two two
Position three-way diverter valve (20) control port pipeline connect, the A port of No. two two-position four way change valves (21) with No. one two four
The control port X-tube road of logical hydraulic pilot reversal valve (22) connects, the B port of No. two two-position four way change valves (21) with No. one two
The control port Y pipeline of position four-way hydraulic pilot reversing valve (22) connects, the B of two-position four-way hydraulic pilot reversal valve (22)
Port is connected with the external-connected port D5 pipeline of control valve group (II), the A port of two-position four-way hydraulic pilot reversal valve (22)
It is connected with the external-connected port D4 pipeline of control valve group (II), the A port of No. two two-position four-ways hydraulic pilot reversal valve (23) and control
The connection of external-connected port D2 pipeline, the B port of No. two two-position four-ways hydraulic pilot reversal valve (23) and the control valve of valve group (II) processed
The external-connected port D3 pipeline of group (II) connects, the external-connected port T3 pipe of the oil-out of No. five overflow valves (24) and control valve group (II)
Road connects.
2. according to the hydraulic hub motor assistant drive system described in claim 1 it is characterised in that described controller (30)
Connect with control valve group (II) circuit and refer to：
The input of the solenoid at No. three three position three-way change valve (17) two ends in control valve group (II) passes through electric wire respectively
It is connected to the port LA05 of controller (30) and the port LA06 of controller (30)；
The input of the solenoid of a two-position four way change valve (18) in control valve group (II) is connected by electrical wiring to control
The port LA07 of device (30) processed；
The input of the solenoid of a two position three way directional control valve (19) in control valve group (II) is connected by electrical wiring to control
The port LA24 of device (30) processed；
The input of the solenoid of No. two two-position four way change valves (21) in control valve group (II) is connected by electrical wiring to control
The port LA25 of device (30) processed.
3. according to the hydraulic hub motor assistant drive system described in claim 1 it is characterised in that described controller (30)
Connect with hydraulic pump module (I) circuit and refer to：
A three position three-way change valve (4) in hydraulic pump module (I) is solenoid directional control valve, the electromagnetic wire in its two ends electric magnet
The input of circle is connected by electrical wiring to the port LA00 of controller (30) and the port LA01 of controller (30) respectively；
No. two three position three-way change valves (5) in hydraulic pump module (I) are solenoid directional control valves, the electromagnetic wire in its two ends electric magnet
The input of circle is connected by electrical wiring to the port LA02 of controller (30) and the port LA03 of controller (30) respectively；
One end away from hydraulic pump (7) of hydraulic cylinder (6) in hydraulic pump module (I) is provided with displacement transducer (s), and displacement passes
The output signal of sensor (s) is connected by holding wire to the port EAD00 of controller (30)；
Bi-bit bi-pass reversal valve (10) in hydraulic pump module (I) is solenoid directional control valve, the solenoid in its electric magnet defeated
Enter the port LA04 that end is connected by electrical wiring to controller (30).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510264263.8A CN104859424B (en) | 2015-05-21 | 2015-05-21 | Hydraulic auxiliary drive system by adopting wheel hub motors |
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| CN201510264263.8A CN104859424B (en) | 2015-05-21 | 2015-05-21 | Hydraulic auxiliary drive system by adopting wheel hub motors |
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| CN104859424B true CN104859424B (en) | 2017-02-22 |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105459804B (en) * | 2015-12-30 | 2017-10-13 | 吉林大学 | Hub motor hydraulic hybrid power system |
| ITUB20160219A1 (en) * | 2016-01-25 | 2017-07-25 | Cnh Ind Italia Spa | Transmission system. |
| CN105818679A (en) * | 2016-03-28 | 2016-08-03 | 吉林大学 | Independent drive wheeled vehicle-based multiwheel multimodal closed-loop hydrostatic drive system |
| CN106939909B (en) * | 2017-05-10 | 2018-04-13 | 吉林大学 | A kind of hydraulic auxiliary driving system of integrated hydraulic starter |
| CN108626187B (en) * | 2018-07-13 | 2024-02-27 | 湖南星邦智能装备股份有限公司 | Hydraulic walking system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1842429A (en) * | 2003-12-23 | 2006-10-04 | 布鲁宁赫斯海诺马帝克有限公司 | Hydrostatic drive system with pump-sided division of the amount of hydraulic fluid for two hydraulic circuits |
| CN101128335A (en) * | 2004-01-30 | 2008-02-20 | 由美国环境保护署署长代表的美利坚合众国政府 | Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof |
| EP1950468A1 (en) * | 2005-11-02 | 2008-07-30 | Hitachi Construction Machinery Co., Ltd | Travel control device for working vehicle and working vehicle |
| CN102358163A (en) * | 2011-08-09 | 2012-02-22 | 吉林大学 | Hydraulic driving system for hub motor |
| CN103407449A (en) * | 2013-08-23 | 2013-11-27 | 吉林大学 | Hydraulic auxiliary driving and braking system and control method thereof |
| CN204659440U (en) * | 2015-05-21 | 2015-09-23 | 吉林大学 | Hydraulic hub motor assistant drive system |
-
2015
- 2015-05-21 CN CN201510264263.8A patent/CN104859424B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1842429A (en) * | 2003-12-23 | 2006-10-04 | 布鲁宁赫斯海诺马帝克有限公司 | Hydrostatic drive system with pump-sided division of the amount of hydraulic fluid for two hydraulic circuits |
| CN101128335A (en) * | 2004-01-30 | 2008-02-20 | 由美国环境保护署署长代表的美利坚合众国政府 | Hydraulic hybrid vehicle with integrated hydraulic drive module and four-wheel-drive, and method of operation thereof |
| EP1950468A1 (en) * | 2005-11-02 | 2008-07-30 | Hitachi Construction Machinery Co., Ltd | Travel control device for working vehicle and working vehicle |
| CN102358163A (en) * | 2011-08-09 | 2012-02-22 | 吉林大学 | Hydraulic driving system for hub motor |
| CN103407449A (en) * | 2013-08-23 | 2013-11-27 | 吉林大学 | Hydraulic auxiliary driving and braking system and control method thereof |
| CN204659440U (en) * | 2015-05-21 | 2015-09-23 | 吉林大学 | Hydraulic hub motor assistant drive system |
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