CN104859424A - Hydraulic auxiliary drive system by adopting wheel hub motors - Google Patents
Hydraulic auxiliary drive system by adopting wheel hub motors Download PDFInfo
- Publication number
- CN104859424A CN104859424A CN201510264263.8A CN201510264263A CN104859424A CN 104859424 A CN104859424 A CN 104859424A CN 201510264263 A CN201510264263 A CN 201510264263A CN 104859424 A CN104859424 A CN 104859424A
- Authority
- CN
- China
- Prior art keywords
- port
- way
- valves
- change
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Fluid-Pressure Circuits (AREA)
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, or rather, the present invention relates to a kind of hydraulic efficiency pressure system adopting hydraulic hub motor to carry out front-wheel assistive drive.
Background technology
Heavy duty truck and engineering truck are everlasting operation on the low adhesion value road surfaces such as sand ground, muddy and ice and snow, and it requires very high to dynamic property.For improving the dynamic property of vehicle, conventional heavy-duty vehicle often adopts a11wheel drive, but system architecture is complicated, and quality is large.At present, have based on hybrid power automobile power system structure proposition all-wheel powered scheme.If China Patent Publication No. is CN101096180A, the day for announcing is 2008-01-02, discloses a kind of four-wheel driven hybrid power system, namely adopts power distribution system, front driving axle, rear driving axle, electrical generator and electrical motor to realize the technology of four wheel drive.But the shortcomings such as present battery power density is little, the life-span is short cause it to be unsuitable for the realization of heavy duty truck.
In the U.S., Japan and the country such as French, as far back as just proposing hydraulic auxiliary driving system 70th century, adopting Hydraulic Pump to obtain power driven HM Hydraulic Motor from driving engine, assistive drive is carried out to vehicle.This system has the clear superiorities such as structure is simple, specific power large, repacking cost is low, should be used for commercial heavy vehicle, and be successfully applied to many moneys vehicle.Assist front axle driving system and wheel hub hydraulic pressure to assist rear-axle drive system as French ripple Crane Co., Ltd proposes wheel hub hydraulic pressure in succession, and be applied on dumping car and tractor truck.Bosch also successfully have developed a set of fluid power traction ancillary system.Although the technology that above-mentioned each system adopts is variant, principle of work is similar, all includes the structures such as Hydraulic Pump, HM Hydraulic Motor, controller and fluid control valve group in system.Wherein the most key parts are exactly fluid control valve group, and system needs under the switching of valve group, to realize different mode of operations, as free gear pattern, assistive drive pattern and bypass mode etc.Current, the domestic research also carried out gradually 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, namely by a set of hydraulic auxiliary driving system, rear-guard vehicle is become the technology of 4 wheel driven configuration.But do not introduce the structure of valve group in this patent in detail.Chinese patent publication No. is CN103790876A, and date of publication is 2114-05-14, discloses a kind of Closed circuit hydraulic transmission system, namely adopts one group of hydraulic valve to realize the technology of the different mode of operation of system.By the mode of operation of solenoid control hub motor in this patent, but the flow of electromagnetic valve is general less, cannot meet the traffic requirement in reality.
Summary of the invention
The present invention solves traditional rear-guard vehicle cannot meet the problem that dynamic property requires, the existing hub hydraulic motor driving system large discharge that cannot meet hub motor requires on low adhesion value road surface and heavy grade road surface, propose a kind of hydraulic hub motor assistant drive system, the present invention adopts following technical scheme to realize:
Hydraulic hub motor assistant drive system, comprise hydraulic pump module, control cock group, controller, power takeoff, power takeoff output shaft, the near front wheel, left wheel hub motor, right hub motor, off front wheel, fuel tank, be that spline pair connects or universal-joint connects between hydraulic pump module input shaft in power takeoff output shaft and hydraulic pump module, the external-connected port T1 of control cock group, T2, T3 is connected to fuel tank by pipeline, the external-connected port L1 of hydraulic pump module, L2, L3 is connected to fuel tank by pipeline, the external-connected port M1 of hydraulic pump module is connected by pipeline with the external-connected port G of control cock group, the external-connected port M2 of hydraulic pump module is connected with the external-connected port A pipeline of control cock group, the external-connected port M3 of hydraulic pump module is connected with the external-connected port B pipeline of control cock group, the external-connected port D1 of control cock group is connected with the housing oil dump port pipeline of the housing oil dump port of left wheel hub motor and right hub motor, the external-connected port D2 of control cock group is connected with a hydraulic fluid port pipeline of left wheel hub motor, the external-connected port D3 of control cock group is connected with another hydraulic fluid port pipeline of left wheel hub motor, the external-connected port D4 of control cock group is connected with a hydraulic fluid port pipeline of right hub motor, the external-connected port D5 of control cock group is connected with another hydraulic fluid port pipeline of right hub motor, spline pair is adopted to be connected between the rotor shaft of left wheel hub motor and the transmission shaft of the near front wheel or both are for same axis, spline pair is adopted to be connected between the rotor shaft of right hub motor and the transmission shaft of off front wheel or both are for same axis, controller is connected by signal wire (SW) with hydraulic pump module, controller is connected with control cock group circuit, controller is connected with hydraulic pump module circuit, it is characterized in that:
Control cock group comprises: No. four by pass valves, No. three three position three-way change valves, a two-position four way change valve, a two position three way directional control valve, No. two two position three way directional control valves, No. two two-position four way change valves, a two-position four-way hydraulic pilot change-over valve, No. two two-position four-way hydraulic pilot change-over valves and No. five by pass valves, wherein, No. three three position three-way change valves, a two-position four way change 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 by pass valves and No. five by pass valves are direct acting type by pass valves, No. two two position three way directional control valves, a two-position four-way hydraulic pilot change-over valve and No. two two-position four-way hydraulic pilot change-over valves are all hydraulic pilot change-over valve,
The T port of No. three three position three-way change valves is connected with No. four by pass valve oil inlet pipelines, the oil outlet of No. four by pass valves is connected with the external-connected port T1 pipeline of control cock group, the P port of No. three three position three-way change valves and the external-connected port A of control cock group, the P port tube of No. two two position three way directional control valves connects, the B port of No. three three position three-way change valves and the external-connected port B of control cock group, the T port of No. two two position three way directional control valves, the P port of a two-position four-way hydraulic pilot change-over valve, the T port tube of No. two two-position four-way hydraulic pilot change-over valves connects, the T port of the B port of No. two two position three way directional control valves and a two-position four-way hydraulic pilot change-over valve, the P port tube of No. two two-position four-way hydraulic pilot change-over valves connects, the P port of a two-position four way change valve and the external-connected port G of control cock group, the P port of a two position three way directional control valve, the P port tube of No. two two-position four way change valves 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, the T port of No. two two-position four way change valves, the external-connected port T2 pipeline of control cock group connects, the control port X of the A port of a two-position four way change valve and No. two two-position four-way hydraulic pilot change-over valves, the oil inlet of No. five by pass valves, the external-connected port D1 pipeline of control cock group connects, 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 change-over valves, 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, the A port of No. two two-position four way change valves is connected with the control port X-tube road of a two-position four-way hydraulic pilot change-over valve, the B port of No. two two-position four way change valves is connected with the control port Y pipeline of a two-position four-way hydraulic pilot change-over valve, the B port of a two-position four-way hydraulic pilot change-over valve is connected with the external-connected port D5 pipeline of control cock group, the A port of a two-position four-way hydraulic pilot change-over valve is connected with the external-connected port D4 pipeline of control cock group, the A port of No. two two-position four-way hydraulic pilot change-over valves is connected with the external-connected port D2 pipeline of control cock group, the B port of No. two two-position four-way hydraulic pilot change-over valves is connected with the external-connected port D3 pipeline of control cock group, the oil outlet of No. five by pass valves is connected with the external-connected port T3 pipeline of control cock group.
Further technical scheme comprises:
Described controller is connected with control cock group circuit and refers to:
The input end of the magnet coil at No. three three position three-way change valve two ends in control cock group is respectively by the port LA06 of the port LA05 and controller that are wired to controller;
The input end of the magnet coil of a two-position four way change valve in control cock group is connected by electrical wiring to the port LA07 of controller;
The input end of the magnet coil of a two position three way directional control valve in control cock group is connected by electrical wiring to the port LA24 of controller;
The input end of the magnet coil of No. two two-position four way change valves in control cock group is connected by electrical wiring to the port LA25 of controller.
Described controller is connected with hydraulic pump module circuit and refers to:
A three position three-way change valve in hydraulic pump module is solenoid directional control valve, and the input end of the magnet coil in its two ends electromagnet is respectively by the port LA01 of the port LA00 and controller that are wired to controller;
No. two three position three-way change valves in hydraulic pump module are solenoid directional control valves, and the input end of the magnet coil in its two ends electromagnet is respectively by the port LA03 of the port LA02 and controller that are wired to controller;
One end away from Hydraulic Pump of hydraulic actuating cylinder in hydraulic pump module is provided with displacement pickup, and the output signal of displacement pickup is connected to the port EAD00 of controller by signal wire (SW);
Bi-bit bi-pass change-over valve in hydraulic pump module is solenoid directional control valve, and the input end of the magnet coil in its electromagnet is connected by electrical wiring to the port LA04 of controller.
Hydraulic hub motor assistant drive system obtains power driven Hydraulic Pump by power takeoff from driving engine, by the control position of controller switching control valve group, thus formation multiple-working mode, as free gear pattern, assistive drive pattern and bypass mode, the control fluid of hydraulicchange-over valve is controlled by solenoid directional control valve, thus control the mode of operation of hub motor, the large discharge requirement of hub motor can be met.
Compared with prior art, the invention has the beneficial effects as follows:
1. vehicle front-wheel can be become drive wheel from non-driving wheel by the hydraulic hub motor assistant drive system that the present invention proposes, and is conducive to the dynamic property improving vehicle.
2. the present invention propose hydraulic hub motor assistant drive system in hydraulic pump module be integrated with main pump and regulate the structures such as the servo-control mechanism of its discharge capacity, oil-supplementing system and by pass valve, HM Hydraulic Motor adopts radial plunger type motor, and be integrated in the wheel hub of front-wheel, whole system scantling of structure is little, take up room little, arrange with installation simple and convenient;
3. the control cock group in the hydraulic hub motor assistant drive system that proposes of the present invention can meet the large discharge requirement of hub motor in Practical Project, can realize hub motor and switch under different conditions, have good adaptability for working condition;
4. in the hydraulic hub motor assistant drive system that the present invention proposes, when hub motor is in free gear state, fluid control valve group can make to retain certain pressure in motor shell, motor piston is thoroughly separated with motor shell, when ensure that motor does not work, additional load can not be applied to front-wheel;
5. in the hydraulic hub motor assistant drive system that the present invention proposes, when vehicle is shifted gears, by control cock group by hub motor bypass, gearshift terminates rear rapid recovery driving condition, the pressure change of motor working connection when which decreasing HM Hydraulic Motor short time switching state, reduce the compression shock of motor shell, improve the work life of HM Hydraulic Motor;
6., in hydraulic hub motor assistant drive system of the present invention, Hydraulic Elements each in control cock group are carried out integrated, reduces the volume shared by hydraulic efficiency pressure system.
Accompanying drawing explanation
Below in conjunction with accompanying drawing, the present invention is further illustrated:
Fig. 1 is the structure principle chart of a kind of hydraulic hub motor assistant drive system of the present invention;
Fig. 2 is hydraulic hub motor assistant drive system control cock group constructional drawing of the present invention;
Fig. 3 is hydraulic hub motor assistant drive system of the present invention each change-over valve control position schematic diagram under free gear pattern;
Fig. 4 is hydraulic hub motor assistant drive system of the present invention each change-over valve control position schematic diagram under assistive drive pattern;
Fig. 5 is hydraulic hub motor assistant drive system of the present invention each change-over valve control position schematic diagram under bypass mode;
Fig. 6 is by simulating, verifying, and the hydraulic hub motor assistant drive system of the present invention obtained increases scale map to the tractive force and climbable gradient that improve car load.
In figure: 1. power takeoff, 2. power takeoff output shaft, 3. hydraulic pump module input shaft, 4. a three position three-way change valve, 5. No. two three position three-way change valves, 6. hydraulic actuating cylinder, 7. Hydraulic Pump, 8. slippage pump, 9. a by pass valve, 10. bi-bit bi-pass change-over valve, No. 11. check valves, 12. No. two by pass valves, 13. No. two check valves, 14. No. three by pass valves, 15. No. three check valves, 16. No. four by pass valves, 17. No. three three position three-way change valves, No. 18. two-position four way change valves, No. 19. two position three way directional control valves, 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 change-over valves, 23. No. two two-position four-way hydraulic pilot change-over valves, 24. No. five by pass valves, 25. the near front wheels, 26. left wheel hub motors, 27. right hub motors, 28. off front wheel, 29. fuel tanks, 30. controllers, S. displacement pickup, I. hydraulic pump module, II. control cock group.
M1, M2, M3, L1, L2, L3 are the external-connected port of hydraulic pump module I, and G, A, B, T1, T2, T3, D1, D2, D3, D4, D5 are the external-connected port of control cock group II.
Detailed description of the invention
Below in conjunction with accompanying drawing, the present invention is described in detail.
Accompanying drawings 1, the hydraulic hub motor assistant drive system that the present invention proposes comprises hydraulic pump module I, control cock 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 27, off front wheel 28, fuel tank 29.
Accompanying drawings 1, power takeoff 1 and power takeoff output shaft 2 provide power for hydraulic pump module I, for mechanical type connects between power takeoff output shaft 2 and hydraulic pump module input shaft 3, connection mode can be common key or spline pair or be connected by universal-joint, the effect of power takeoff 1 and power takeoff output shaft 2 is by transmission of power to hydraulic pump module I, thus makes hydraulic pump module I export steady fluid.
Accompanying drawings 1, hydraulic pump module I comprises: hydraulic pump module input shaft 3, three position three-way change valve 4, No. two three position three-way change valves 5, hydraulic actuating cylinder 6, Hydraulic Pump 7, slippage pump 8, a by pass valve 9, bi-bit bi-pass change-over valve 10, check valve 11, No. two by pass valves 12, No. two check valves 13, No. three by pass valves 14, No. three check valves 15.Wherein, hydraulic actuating cylinder 6 is hydraulic cylinder with double piston rods; Hydraulic Pump 7 is axial piston bidirectional variable Hydraulic Pump; Slippage pump 8 is unidirectional quantitative gear pump; A three position three-way change valve 4 and No. two three position three-way change valves 5 are all solenoid directional control valves; A by pass valve 9, No. two by pass valves 12 and No. three by pass valves 14 are all direct acting type by pass valves; A check valve 11, No. two check valves 13 and No. three check valves 15 are direct-drive one-way valve.
Accompanying drawings 1, hydraulic pump module input shaft 3 is same axis with the rotor shaft of Hydraulic Pump 7, slippage pump 8, the T port of the T port of a three position three-way change valve 4 and No. two three position three-way change valves 5, the external-connected port L1 pipeline of hydraulic pump module I connects, the P port of the P port of a three position three-way change valve 4 and No. two three position three-way change valves 5, slippage pump 8 oil outlet pipeline connects, the A port of a three position three-way change valve 4 is connected with a hydraulic fluid port pipeline of hydraulic actuating cylinder 6, another hydraulic fluid port of hydraulic actuating cylinder 6 is connected with the A port tube of No. two three position three-way change valves 5, one end of hydraulic actuating cylinder 6 piston rod adopts ball pivot to be connected with the swash plate of Hydraulic Pump 7, the oil inlet of the oil outlet of slippage pump 8 and a by pass valve 9, the P port tube of bi-bit bi-pass change-over valve 10 connects, the A port of bi-bit bi-pass change-over valve 10 and check valve 11 oil inlet, No. two by pass valve 12 oil outlets, No. two check valve 13 oil inlets, No. three by pass valve 14 oil outlets, No. three check valve 15 oil inlet pipelines connect, No. three check valve 15 oil outlets are connected with the external-connected port M1 pipeline of hydraulic pump module I, a hydraulic fluid port of Hydraulic Pump 7 and check valve 11 oil outlet, No. two by pass valve 12 oil inlets, the external-connected port M2 pipeline of hydraulic pump module I connects, another hydraulic fluid port of Hydraulic Pump 7 and No. two check valve 13 oil outlets, No. three by pass valve 14 oil inlets, the external-connected port M3 pipeline of hydraulic pump module I connects, the oil inlet of slippage pump 8 is connected with the external-connected port L2 pipeline of hydraulic pump module I, the oil outlet of a by pass valve 9 is connected with the external-connected port L3 pipeline of hydraulic pump module I.
Accompanying drawings 2, control cock group II comprises: No. four by pass valves 16, No. three three position three-way change valves 17, a two-position four way change valve 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, a two-position four-way hydraulic pilot change-over valve 22, No. two two-position four-way hydraulic pilot change-over valves 23, No. five by pass 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 valve 19 and No. two two-position four way change valves 21 are all solenoid directional control valve; No. four by pass valves 16 and No. five by pass valves 24 are direct acting type by pass valves; No. two two position three way directional control valves 20, two-position four-way hydraulic pilot change-over valve 22 and No. two two-position four-way hydraulic pilot change-over valves 23 are all hydraulic pilot change-over valve.
Accompanying drawings 2, the T port of No. three three position three-way change valves 17 is connected with No. four by pass valve 16 oil inlet pipelines, No. four by pass valve 16 oil outlets are connected with the external-connected port T1 pipeline of control cock group II, the P port of No. three three position three-way change valves 17 and the external-connected port A of control cock group II, the P port tube of No. two two position three way directional control valves 20 connects, the B port of No. three three position three-way change valves 17 and the external-connected port B of control cock group II, the T port of No. two two position three way directional control valves 20, the P port of a two-position four-way hydraulic pilot change-over valve 22, the T port tube of No. two two-position four-way hydraulic pilot change-over valves 23 connects, the T port of the B port of No. two two position three way directional control valves 20 and a two-position four-way hydraulic pilot change-over valve 22, the P port tube of No. two two-position four-way hydraulic pilot change-over valves 23 connects, the P port of a two-position four way change valve 18 and the external-connected port G of control cock group II, the P port of a two position three way directional control valve 19, the P port tube of No. two two-position four way change valves 21 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, the T port of No. two two-position four way change valves 21, the external-connected port T2 pipeline of control cock group II connects, the control port X of the A port of a two-position four way change valve 18 and No. two two-position four-way hydraulic pilot change-over valves 23, No. five by pass valve 24 oil inlets, the external-connected port D1 pipeline of control cock group II connects, the B port of a two-position four way change valve 18 is connected with the control port Y pipeline of No. two two-position four-way hydraulic pilot change-over valves 23, the T port of a two position three way directional control valve 19 is connected with the control port pipeline of No. two two position three way directional control valves 20, the A port of No. two two-position four way change valves 21 is connected with the control port X-tube road of a two-position four-way hydraulic pilot change-over valve 22, the B port of No. two two-position four way change valves 21 is connected with the control port Y pipeline of a two-position four-way hydraulic pilot change-over valve 22, the B port of a two-position four-way hydraulic pilot change-over valve 22 is connected with the external-connected port D5 pipeline of control cock group II, the A port of a two-position four-way hydraulic pilot change-over valve 22 is connected with the external-connected port D4 pipeline of control cock group II, the A port of No. two two-position four-way hydraulic pilot change-over valves 23 is connected with the external-connected port D2 pipeline of control cock group II, the B port of No. two two-position four-way hydraulic pilot change-over valves 23 is connected with the external-connected port D3 pipeline of control cock group II, No. five by pass valve 24 oil outlets are connected with the external-connected port T3 pipeline of control cock group II.
Accompanying drawings 3, controller 30 existing procucts, concrete type selecting can be determined by actual conditions, is HY-TTC200-CD-538K-2.4M-WD00-000 in this controller used thereby model.Controller 30, for the output signal of received bit displacement sensor s, controls the control position of a three position three-way change valve 4, No. two three position three-way change valves 5, bi-bit bi-pass change-over valve 10, No. three three position three-way change valves 17, two-position four way change valve 18, two position three way directional control valve 19, No. two two-position four way change valves 21 simultaneously.
Accompanying drawings 3, a three position three-way change valve 4 is solenoid directional control valve, and electromagnet is handled, spring reset, and the input end of the magnet coil in its two ends electromagnet is respectively by the port LA01 of the port LA00 and controller 30 that are wired to controller 30; No. two three position three-way change valves 5 are solenoid directional control valves, and the input end of the magnet coil in its two ends electromagnet is respectively by the port LA03 of the port LA02 and controller 30 that are wired to controller 30; The other end away from Hydraulic Pump 7 of hydraulic actuating cylinder 6 is provided with displacement pickup s, and the cylinder body of hydraulic actuating cylinder is fixed on the housing of hydraulic pump module I mechanically, and the output signal of displacement pickup s is by being wired to the port EAD00 of controller 30; Bi-bit bi-pass change-over valve 10 is solenoid directional control valves, and the input end of the magnet coil in its electromagnet is connected by electrical wiring to the port LA04 of controller 30; No. three three position three-way change valves 17, two-position four way change valve 18, two position three way directional control valve 19 and No. two two-position four way change valves 21 are all solenoid directional control valves; The input end of the magnet coil at No. three three position three-way change valve 17 two ends is respectively by the port LA06 of the port LA05 and controller 30 that are wired to controller 30; The input end of the magnet coil of a two-position four way change valve 18 is connected by electrical wiring to the port LA07 of controller 30; The input end of the magnet coil of a two position three way directional control valve 19 is connected by electrical wiring to the port LA24 of controller 30; The input end of the magnet coil of No. two two-position four way change valves 21 is connected by electrical wiring to the port LA25 of controller 30.
Accompanying drawings 3, external-connected port T1, T2, T3 of control cock group II are connected to fuel tank 29 by pipeline; External-connected port L1, L2, L3 of hydraulic pump module I are connected to fuel tank 29 by pipeline; The external-connected port M1 of hydraulic pump module I is connected with the external-connected port G pipeline of control cock group II, the external-connected port M2 of hydraulic pump module I is connected with the external-connected port A pipeline of control cock group II, and the external-connected port M3 of hydraulic pump module I is connected with the external-connected port B pipeline of control cock group II.
Accompanying drawings 3, the external-connected port D1 of control cock group II is connected with the housing oil dump port pipeline of the housing oil dump port of left wheel hub motor 26, right hub motor 27; The external-connected port D2 of control cock group II is connected with a hydraulic fluid port pipeline of left wheel hub motor 26; The external-connected port D3 of control cock group II is connected with another hydraulic fluid port pipeline of left wheel hub motor 26; The external-connected port D4 of control cock group II is connected with a hydraulic fluid port pipeline of right hub motor 27; The external-connected port D5 of control cock group II is connected with another hydraulic fluid port pipeline of right hub motor 27; Left wheel hub motor 26 is radial plunger type two-way quantitative motors, adopts spline pair to be connected or both are for same axis between its rotor shaft and the transmission shaft of the near front wheel 25; Right hub motor 27 is also radial plunger type two-way quantitative motor, adopts spline pair to be connected or both are for same axis between its rotor shaft and the transmission shaft of off front wheel 28;
Accompanying drawings 3, power takeoff 1 and power takeoff output shaft 2 provide prime power for hydraulic auxiliary driving system, drive Hydraulic Pump 7 and slippage pump 8 to rotate; Hydraulic Pump 7 is bidirectional variable Hydraulic Pumps, and two hydraulic fluid port both can be oil inlet, also can be oil outlet, but operationally only has an oil outlet and an oil inlet, and the discharge capacity of Hydraulic Pump 7 drives swash plate aperture to regulate by the piston rod of hydraulic actuating cylinder 6; The housing of hydraulic actuating cylinder 6 adopts mechanical system to fix, and the displacement of piston rod is passed to controller 30 by displacement pickup s, and controller 30 obtains the feedback discharge capacity of Hydraulic Pump 7 by the signal value of displacement pickup s, thus forms closed loop control; Slippage pump 8 is unidirectional quantitative hydraulic pumps, and its effect is to system circuit repairing, simultaneously for control cock group II provides control fluid; A check valve 11, No. two by pass valves 12, No. two check valves 13 and No. three by pass valves 14, for only allowing fluid from the A port flow of bi-bit bi-pass change-over valve 10 to working connection, ensure the safety of working connection simultaneously; When bi-bit bi-pass change-over valve 10 switches to bottom, the output fluid of slippage pump 8 through the P port flow of bi-bit bi-pass change-over valve 10 to the oil inlet of No. three check valves 15, export from the external-connected port M1 of hydraulic pump module I after No. three check valves 15, thus control oil for a two-position four-way hydraulic pilot change-over valve 22 and No. two two-position four-way hydraulic pilot change-over valves 23 provide, and control fluid (now a two position three way directional control valve 19 switches to right position) by a two position three way directional control valve 19 for No. two two position three way directional control valves 20 provide.A by pass valve 9 is arranged between the oil outlet of slippage pump 8 and fuel tank 29, to limit the oil outlet pressure of slippage pump 8, thus reaches the object of protection slippage pump 8.
Accompanying drawings 3, the piston movement of hydraulic control cylinder 6 is carried out by the control position controlling a three position three-way change valve 4 and No. two three position three-way change valves 5, thus the swash plate aperture of change Hydraulic Pump 7 is to reach the object changing discharge capacity, the input fluid of a three position three-way change valve 4 and No. two three position three-way change valves 5 is provided by slippage pump 8.When controller 30 exports control command, 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, is now disconnected hydraulic actuating cylinder 6 with the oil circuit between slippage pump 8 simultaneously, hydraulic actuating cylinder 6 two ends are all communicated with fuel tank 29, and now the discharge capacity of Hydraulic Pump 7 is 0.When utilizing controller 30 that a three position three-way change valve 4 and No. two three position three-way change valves 5 are all switched to meta, now pressurize is carried out to the hydraulic pressure at hydraulic actuating cylinder 6 piston two ends, then represent that the discharge capacity keeping Hydraulic Pump 7 is stablized.If switch to upper by a three position three-way change valve 4, No. two three position three-way change valves 5 are switched to bottom, then the piston of hydraulic actuating cylinder 6 moves down, and now the discharge capacity signal value of Hydraulic Pump 7 increases gradually in 0 ~+1 scope.If a three position three-way change valve 4 is switched to bottom, switch to upper by No. two three position three-way change valves 5, the piston of now then hydraulic actuating cylinder 6 moves, and the discharge capacity signal value of Hydraulic Pump 7 increases (absolute value increase) gradually in-1 ~ 0 scope.Controller 30 obtains the displacement of hydraulic actuating cylinder 6 piston rod by the displacement pickup s be arranged on hydraulic actuating cylinder 6 piston rod, itself and expected value is compared and forms closed loop control.
Accompanying drawings 3, when oil liquid temperature rises to certain threshold value in system, exports control command by controller 30, switch the control position of No. three three position three-way change valves 17, partial high pressure fluid is unloaded, carries out repairing by slippage pump 8 pairs of working connections, thus reach the object of cooling.Be specially: when the vehicle is moving in a forward direction, No. three three position three-way change valves 17 are switched to upper, when vehicle backing travels, No. three three position three-way change valves 17 are switched to bottom.
Control signal is exported by controller 30, make a three position three-way change valve 4, No. two three position three-way change valves 5, bi-bit bi-pass change-over valve 10, No. three three position three-way change valves 17, two-position four way change valve 18, two position three way directional control valve 19, No. two two-position four way change valves 21 are in different control positioies, system can be made to realize three kinds of different operational modes, namely free gear pattern, assistive drive pattern and bypass mode, introduce below in detail.
Free gear pattern:
Accompanying drawings 3, now hydraulic hub motor assistant drive system works in free gear pattern.
Control command is exported by controller 30, a three position three-way change valve 4 is switched to bottom, No. two three position three-way change valves 5 switch to bottom, bi-bit bi-pass change-over valve 10 switches to bottom, No. three three position three-way change valves 17 switch to meta, a two-position four way change valve 18 switches to upper, 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 bottom.Slippage pump 8 draws fluid by the external-connected port L2 of hydraulic pump module I from fuel tank 29, by bi-bit bi-pass change-over valve 10, No. three check valves 15, respectively through the Y end of the X end and a two-position four-way hydraulic pilot change-over valve 22 that act on No. two two-position four-way hydraulic pilot change-over valves 23 after a two-position four way change valve 18 and No. two two-position four way change valves 21 after the external-connected port M1 of the hydraulic pump module I and external-connected port G of control cock group II, a two-position four-way hydraulic pilot change-over valve 22 is switched to bottom, No. two two-position four-way hydraulic pilot change-over valves 23 are switched to upper, left wheel hub motor 26 and right hub motor 27 is caused to disconnect with working connection, simultaneously, the A port of a two-position four way change valve 18 is delivered to the housing of left wheel hub motor 26 and right hub motor 27 by the external-connected port D1 of control cock group II, thus make left wheel hub motor 26 inside contract with the plunger of right hub motor 27 and be separated with housing, No. five by pass valves 24 for pressure being limited in suitable scope, to ensure safety, now, hydraulic actuating cylinder 6 piston two ends are all communicated with fuel tank 29, and the discharge capacity of Hydraulic Pump 7 is 0.
Assistive drive pattern:
Accompanying drawings 4, now hydraulic hub motor assistant drive system works in assistive drive pattern.
Control command is exported by controller 30, bi-bit bi-pass change-over valve 10 is switched to bottom, the control position of No. three three position three-way change valves 17 is indefinite (according to system status, can switch to the one in upper, meta and bottom), a two-position four way change valve 18 switches to bottom, 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; Under the effect controlling fluid, a two-position four-way hydraulic pilot change-over valve 22 switches to upper, and No. two two-position four-way hydraulic pilot change-over valves 23 are switched to bottom, and now left wheel hub motor 26 is connected with working connection with right hub motor 27.Hydraulic Pump 7, No. two two position three way directional control valves 20, No. two two-position four-way hydraulic pilot change-over valves 23 and left wheel hub motor 26 form closed loop, realize driving left wheel hub motor 26 to rotate, and closely drive the near front wheel 25 to travel; In like manner, Hydraulic Pump 7, No. two two position three way directional control valves 20, two-position four-way hydraulic pilot change-over valve 22 and right hub motor 27 form loop, thus drive off front wheel 28 to travel.Controller 30 carrys out the displacement of hydraulic control cylinder 6 piston by the control position switching a three position three-way change valve 4 and No. two three position three-way change valves 5, thus reach the object of regulator solution press pump 7 discharge capacity, be specially: if a three position three-way change valve 4 is switched to upper, No. two three position three-way change valves 5 are switched to bottom, then Hydraulic Pump 7 drives left wheel hub motor 26 and the running of right hub motor 27 forward, now vehicle forward travel; If a three position three-way change valve 4 is switched to bottom, switch to upper by No. two three position three-way change valves 5, then Hydraulic Pump 7 drives left wheel hub motor 26 and right hub motor 27 antiport, and now vehicle backing travels.The discharge capacity of control position needed for Hydraulic Pump 7 of a three position three-way change valve 4 and No. two three position three-way change valves 5 is determined.
Bypass mode:
Accompanying drawings 5, now hydraulic hub motor assistant drive system works in bypass mode.
When system works is in assistive drive pattern, when vehicle is shifted gears, hydraulic hub motor assistant drive system is switched to bypass mode, now only need be changed the control position of a two position three way directional control valve 19 by the output signal of controller 30, the control position of other part (as change-over valve, Hydraulic Pump, motor etc.) is constant.Because vehicle only has one to reverse gear, shift process is there is not in vehicle backing travels, switching to by reversing gear in advance gear process, needing to switch when the speed of a motor vehicle is zero, so hydraulic hub motor assistant drive system does not exist bypass mode when vehicle backing travels.When vehicle is shifted gears in moving forward, a two position three way directional control valve 19 is switched to right position, the now T port of a two position three way directional control valve 19 and the conducting of P port, No. two two position three way directional control valves 20 are switched to bottom, the high pressure oil being now delivered to left wheel hub motor 26 and right hub motor 27 is cut off, and hydraulic hub motor assistant drive system works in bypass mode.A three position three-way change valve 4 and No. two three position three-way change valves 5 are in the invariant position at the previous moment place switching to bypass mode.
Element used all existing procucts in the present invention, concrete type selecting need be determined in conjunction with whole-car parameters and designing requirement, and table 1 is car load basic specification and the designing requirement of certain heavy-duty vehicle, and table 2 is the parameter of selected main hydraulic.
Table 1 car load basic specification and designing requirement
Table 2 main hydraulic parameter
For verifying the feasibility of hydraulic hub motor assistant drive system of the present invention, by emulation testing the present invention to the contribution improving power performance.
Show when after employing hydraulic hub motor assistant drive system of the present invention in accompanying drawings 6, figure, the increase ratio of power performance.In figure, solid line represents that tractive force increases the change curve of ratio with coefficient of road adhesion, and dotted line represents that maximum climbable gradient of vehicle increases the change curve of ratio with coefficient of road adhesion.Can find out, when after employing hydraulic hub motor assistant drive system of the present invention, max. climb slope and the tractive force of vehicle are improved significantly, and on low adhesion value road surface, effect is more obvious.
Hydraulic hub motor assistant drive system of the present invention can realize free gear pattern, assistive drive pattern and bypass mode, and under each mode of operation, in control cock group II, the control position of change-over valve is as shown in table 3 below:
The control position of change-over 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 the position signal decision systems of the speed of a motor vehicle, acceleration pedal, different mode of operations is realized by the control position of change-over valve each in switching control valve group II, the discharge capacity of regulator solution press pump 7 is carried out, with satisfied driving demand by the control position controlling a three position three-way change valve 4 and No. two three position three-way change valves 5.
2., when vehicle travels on low adhesion value road surface or climbing, by the control position of each change-over valve in controller 30 switching control valve group II, make system works in assistive drive pattern, now vehicle front-wheel becomes drive wheel, adds vehicle drive force.
3. when vehicle travels in good road surface, hydraulic hub motor assistant drive system works in free gear pattern, and now front-wheel is flower wheel, and this contributes to improving car load drawbar efficiency.
4. when vehicle shift, hydraulic hub motor assistant drive system works in bypass mode, thus ensures that gearshift steadily completes.
5. hydraulic hub motor assistant drive system of the present invention can produce certain heat at work unavoidably, for ensureing system reliable operation, can be reached the object of cooling by the control position switching No. three three position three-way change valves 17.
Can find out according to above principle features, vehicle refitting, on traditional rear wheel drive vehicle basis, by adding a set of hydraulic hub motor assistant drive system, is become four-wheel drive system by the present invention, contributes to improving car load dynamic property.Meanwhile, control cock group II structure of the present invention can meet Practical Project requirement, effectively can control the work of huge discharge hydraulic hub motor, make it steadily export driving torque, have good adaptability for working condition.
Claims (3)
1. hydraulic hub motor assistant drive system, comprise hydraulic pump module (I), control cock group (II), controller (30), power takeoff (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), be that spline pair connects or universal-joint connects between hydraulic pump module input shaft (3) in power takeoff output shaft (2) and hydraulic pump module (I), the external-connected port T1 of control cock group (II), T2, T3 is connected to fuel tank (29) by pipeline, the external-connected port L1 of hydraulic pump module (I), L2, L3 is connected to fuel tank (29) by pipeline, the external-connected port M1 of hydraulic pump module (I) is connected by pipeline with the external-connected port G of control cock group (II), the external-connected port M2 of hydraulic pump module (I) is connected with the external-connected port A pipeline of control cock group (II), the external-connected port M3 of hydraulic pump module (I) is connected with the external-connected port B pipeline of control cock group (II), the external-connected port D1 of control cock group (II) is connected with the housing oil dump port pipeline of the housing oil dump port of left wheel hub motor (26) and right hub motor (27), the external-connected port D2 of control cock group (II) is connected with a hydraulic fluid port pipeline of left wheel hub motor (26), the external-connected port D3 of control cock group (II) is connected with another hydraulic fluid port pipeline of left wheel hub motor (26), the external-connected port D4 of control cock group (II) is connected with a hydraulic fluid port pipeline of right hub motor (27), the external-connected port D5 of control cock group (II) is connected with another hydraulic fluid port pipeline of right hub motor (27), spline pair is adopted to be connected between the rotor shaft of left wheel hub motor (26) and the transmission shaft of the near front wheel (25) or both are for same axis, spline pair is adopted to be connected between the rotor shaft of right hub motor (27) and the transmission shaft of off front wheel (28) or both are for same axis, controller (30) is connected by signal wire (SW) with hydraulic pump module (I), controller (30) is connected with control cock group (II) circuit, controller (30) is connected with hydraulic pump module (I) circuit, it is characterized in that:
Control cock group (II) comprising: No. four by pass valves (16), No. three three position three-way change valves (17), a two-position four way change 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), a two-position four-way hydraulic pilot change-over valve (22), No. two two-position four-way hydraulic pilot change-over valves (23) and No. five by pass valves (24), wherein, No. three three position three-way change valves (17), a two-position four way change valve (18), a two position three way directional control valve (19) and No. two two-position four way change valves (21) are all solenoid directional control valve, No. four by pass valves (16) and No. five by pass valves (24) are direct acting type by pass valves, No. two two position three way directional control valves (20), a two-position four-way hydraulic pilot change-over valve (22) and No. two two-position four-way hydraulic pilot change-over valves (23) are all hydraulic pilot change-over valve,
The T port of No. three three position three-way change valves (17) is connected with No. four by pass valve (16) oil inlet pipelines, the oil outlet of No. four by pass valves (16) is connected with the external-connected port T1 pipeline of control cock group (II), the P port of No. three three position three-way change valves (17) and the external-connected port A of control cock group (II), the P port tube of No. two two position three way directional control valves (20) connects, the B port of No. three three position three-way change valves (17) and the external-connected port B of control cock group (II), the T port of No. two two position three way directional control valves (20), the P port of a two-position four-way hydraulic pilot change-over valve (22), the T port tube of No. two two-position four-way hydraulic pilot change-over valves (23) connects, the B port of No. two two position three way directional control valves (20) and the T port of a two-position four-way hydraulic pilot change-over valve (22), the P port tube of No. two two-position four-way hydraulic pilot change-over valves (23) connects, the P port of a two-position four way change valve (18) and the external-connected port G of control cock group (II), the P port of a two position three way directional control valve (19), the P port tube of No. two two-position four way change valves (21) connects, the T port of a two-position four way change valve (18) and the A port of a two position three way directional control valve (19), the T port of No. two two-position four way change valves (21), the external-connected port T2 pipeline of control cock group (II) connects, the A port of a two-position four way change valve (18) and the control port X of No. two two-position four-way hydraulic pilot change-over valves (23), the oil inlet of No. five by pass valves (24), the external-connected port D1 pipeline of control cock group (II) connects, the B port of a two-position four way change valve (18) is connected with the control port Y pipeline of No. two two-position four-way hydraulic pilot change-over valves (23), the T port of a two position three way directional control valve (19) is connected with the control port pipeline of No. two two position three way directional control valves (20), the A port of No. two two-position four way change valves (21) is connected with the control port X-tube road of a two-position four-way hydraulic pilot change-over valve (22), the B port of No. two two-position four way change valves (21) is connected with the control port Y pipeline of a two-position four-way hydraulic pilot change-over valve (22), the B port of a two-position four-way hydraulic pilot change-over valve (22) is connected with the external-connected port D5 pipeline of control cock group (II), the A port of a two-position four-way hydraulic pilot change-over valve (22) is connected with the external-connected port D4 pipeline of control cock group (II), the A port of No. two two-position four-way hydraulic pilot change-over valves (23) is connected with the external-connected port D2 pipeline of control cock group (II), the B port of No. two two-position four-way hydraulic pilot change-over valves (23) is connected with the external-connected port D3 pipeline of control cock group (II), the oil outlet of No. five by pass valves (24) is connected with the external-connected port T3 pipeline of control cock group (II).
2. according to hydraulic hub motor assistant drive system according to claim 1, it is characterized in that, described controller (30) is connected with control cock group (II) circuit and refers to:
The input end of the magnet coil at No. three three position three-way change valve (17) two ends in control cock group (II) is respectively by the port LA06 of the port LA05 and controller (30) that are wired to controller (30);
The input end of the magnet coil of a two-position four way change valve (18) in control cock group (II) is connected by electrical wiring to the port LA07 of controller (30);
The input end of the magnet coil of a two position three way directional control valve (19) in control cock group (II) is connected by electrical wiring to the port LA24 of controller (30);
The input end of the magnet coil of No. two two-position four way change valves (21) in control cock group (II) is connected by electrical wiring to the port LA25 of controller (30).
3. according to hydraulic hub motor assistant drive system according to claim 1, it is characterized in that, described controller (30) is connected with hydraulic pump module (I) circuit and refers to:
A three position three-way change valve (4) in hydraulic pump module (I) is solenoid directional control valve, and the input end of the magnet coil in its two ends electromagnet is respectively by the port LA01 of the port LA00 and controller (30) that are wired to controller (30);
No. two three position three-way change valves (5) in hydraulic pump module (I) are solenoid directional control valves, and the input end of the magnet coil in its two ends electromagnet is respectively by the port LA03 of the port LA02 and controller (30) that are wired to controller (30);
One end away from Hydraulic Pump (7) of hydraulic actuating cylinder (6) in hydraulic pump module (I) is provided with displacement pickup (s), and the output signal of displacement pickup (s) is connected to the port EAD00 of controller (30) by signal wire (SW);
Bi-bit bi-pass change-over valve (10) in hydraulic pump module (I) is solenoid directional control valve, and the input end of the magnet coil in its electromagnet is connected by electrical wiring to the port LA04 of controller (30).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510264263.8A CN104859424B (en) | 2015-05-21 | 2015-05-21 | Hydraulic auxiliary drive system by adopting wheel hub motors |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510264263.8A CN104859424B (en) | 2015-05-21 | 2015-05-21 | Hydraulic auxiliary drive system by adopting wheel hub motors |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104859424A true CN104859424A (en) | 2015-08-26 |
| CN104859424B CN104859424B (en) | 2017-02-22 |
Family
ID=53905773
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510264263.8A Expired - Fee Related CN104859424B (en) | 2015-05-21 | 2015-05-21 | Hydraulic auxiliary drive system by adopting wheel hub motors |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104859424B (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105459804A (en) * | 2015-12-30 | 2016-04-06 | 吉林大学 | Hub motor hydraulic hybrid power 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 |
| CN106939909A (en) * | 2017-05-10 | 2017-07-11 | 吉林大学 | A kind of hydraulic auxiliary driving system of integrated hydraulic starter |
| CN108602431A (en) * | 2016-01-25 | 2018-09-28 | 凯斯纽荷兰(中国)管理有限公司 | Transmission system |
| CN108626187A (en) * | 2018-07-13 | 2018-10-09 | 湖南星邦重工有限公司 | A kind of hydraulic travel system |
| CN112610560A (en) * | 2020-12-16 | 2021-04-06 | 北京玖鼎力源科技有限公司 | Test bed for hydraulic motor, hydraulic pump and rear axle |
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 |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105459804A (en) * | 2015-12-30 | 2016-04-06 | 吉林大学 | Hub motor hydraulic hybrid power system |
| CN105459804B (en) * | 2015-12-30 | 2017-10-13 | 吉林大学 | Hub motor hydraulic hybrid power system |
| CN108602431A (en) * | 2016-01-25 | 2018-09-28 | 凯斯纽荷兰(中国)管理有限公司 | Transmission system |
| US10926631B2 (en) | 2016-01-25 | 2021-02-23 | Cnh Industrial America Llc | 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 |
| CN106939909A (en) * | 2017-05-10 | 2017-07-11 | 吉林大学 | A kind of hydraulic auxiliary driving system of integrated hydraulic starter |
| CN108626187A (en) * | 2018-07-13 | 2018-10-09 | 湖南星邦重工有限公司 | A kind of hydraulic travel system |
| 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 |
| CN112610560A (en) * | 2020-12-16 | 2021-04-06 | 北京玖鼎力源科技有限公司 | Test bed for hydraulic motor, hydraulic pump and rear axle |
| CN112610560B (en) * | 2020-12-16 | 2024-05-31 | 北京玖鼎力源科技有限公司 | Test bed for hydraulic motor, hydraulic pump and rear axle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104859424B (en) | 2017-02-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104859424A (en) | Hydraulic auxiliary drive system by adopting wheel hub motors | |
| CN103407449B (en) | A kind of hydraulic pressure assistive drive and brake system and control method thereof | |
| CN103569098B (en) | Hydraulic pressure process auxiliary drive and brakes and control method thereof | |
| CN105459804B (en) | Hub motor hydraulic hybrid power system | |
| CN108248599B (en) | Hydraulic hybrid regeneration brake system and control method based on double accumulators | |
| CN103568810A (en) | Energy recyclable auxiliary hub motor hydraulic driving system and control method thereof | |
| CN103790875B (en) | A kind of Hydraulic Power Transmission System allowing energy regenerating | |
| CN108128212B (en) | Hydraulic auxiliary driving/braking system for electric automobile and control method thereof | |
| CN203528285U (en) | Hydraulic auxiliary hub motor drive system with energy recovery capacity | |
| CN103790876B (en) | A kind of Closed circuit hydraulic transmission system | |
| KR20170061674A (en) | Dual drive driveline | |
| CN201320956Y (en) | Four-wheel fully-driven hydraulic hybrid power transmission device of bus | |
| CN105459978B (en) | Hydraulic pressure process auxiliary drive and brake energy recovering system | |
| CN204659440U (en) | Hydraulic hub motor assistant drive system | |
| CN203717498U (en) | Hydraulic transmission system capable of allowing energy recovery | |
| CN203439027U (en) | Hydraulic auxiliary drive and brake system | |
| CN105216615B (en) | A kind of hybrid power drive axle | |
| CN105818679A (en) | Independent drive wheeled vehicle-based multiwheel multimodal closed-loop hydrostatic drive system | |
| CN203651750U (en) | Hydraulic auxiliary driving and braking system | |
| CN2736202Y (en) | Tandem type hydraulic mixed power transmitting means for public transport automobile | |
| CN110758096A (en) | Wheel hub drive hydraulic hybrid vehicle configuration system | |
| CN105437947B (en) | Trackless rubber-tyred command car | |
| CN109649163A (en) | Vehicle to run system and its control method, environmental sanitation vehicles | |
| CN205273184U (en) | Hydrostatic 4 wheel driven system of trolley -bus rubber tyer command car | |
| CN203717499U (en) | Closed type hydraulic transmission system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| EXSB | Decision made by sipo to initiate substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20170222 Termination date: 20190521 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |