CN102635144B - Hydraulic system for loader - Google Patents
Hydraulic system for loader Download PDFInfo
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- CN102635144B CN102635144B CN201210135603.3A CN201210135603A CN102635144B CN 102635144 B CN102635144 B CN 102635144B CN 201210135603 A CN201210135603 A CN 201210135603A CN 102635144 B CN102635144 B CN 102635144B
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Abstract
The invention discloses a hydraulic system of a loader. The hydraulic system comprises a hydraulic pump, a low pressure sealed oil tank, a high pressure energy accumulator, a medium pressure energy accumulator and a hydraulic control unit, wherein the hydraulic control unit is integrated with a first one-way valve, a second one-way valve, a third one-way valve, a first safety valve, a second safety valve, a third safety valve, a first pressure sensor, a second pressure sensor, a first magnetic exchange valve, a second magnetic exchange valve, a third magnetic exchange valve, a first magnetic proportional exchange valve, a second magnetic proportional exchange valve, a third magnetic proportional exchange valve and a fourth magnetic proportional exchange valve. The hydraulic system for the loader provided by the invention utilizes the high pressure energy accumulator and the medium pressure energy accumulator to store kinetic energy in the braking process of loader and excess energy of the loader in low load conditions and stores potential energy of the movable arm in the falling process by the low pressure sealed oil tank, thereby achieving the purposes of reducing fuel consumption of the loader and increasing working efficiency of the loader.
Description
Technical field
The present invention relates to a kind of hydraulic system, more particularly, the present invention relates to a kind of loader hydraulic system.。
Background technology
Loader is widely used in the construction such as mining site, capital construction, road maintenance occasion, is mainly that to shovel bulk materials such as filling native stone, mineral be main.Because it is simple and convenient, can save in a large number manpower, to increase work efficiency, loader has become important engineering machinery.
In prior art, loader hydraulic system comprises that hydraulic pump, boom cylinder, rotary ink tank, safety valve, oil filter, double-acting safety valve, swing arm manually join guiding valve, rotating bucket and manually join guiding valve and open type oil tank.Loading operation process comprise travel, spading, moved arm lifting, the scraper bowl that falls, the swing arm that falls etc. carry out cycle operation, the wherein engine load of spading process need maximum, although and swing arm decline process is because the existence of gravitional force does not need the driving of motor, but existing loader still drives hydraulic pump works to complete swing arm decline process by engine running, and can not reclaim the potential energy that swing arm falls, braking procedure also cannot be recycled the kinetic energy of loader, thus make the oil consumption of loader high, loading operation efficiency is low.
Summary of the invention
The object of the invention is to overcome above-mentioned defect, a kind of oil consumption of loader, loader hydraulic system of raising loading operation efficiency of reducing is provided.
For solving the problems of the technologies described above, the present invention, by adopting high pressure accumulator, intermediate-pressure accumulator, low pressure sealed reservoir and hydraulic control unit, realizes storage, distribution, recovery and the release of hydraulic energy, and its technical scheme is:
A kind of loader hydraulic system, comprises hydraulic pump, low pressure sealed reservoir, high pressure accumulator, intermediate-pressure accumulator, hydraulic control unit, boom cylinder, rotary ink tank, oil filter;
High pressure accumulator adopts piston type or bladder accumulator, and the operating pressure of high pressure accumulator is 16～35MPa, and intermediate-pressure accumulator adopts piston type or bladder accumulator, and the operating pressure of intermediate-pressure accumulator is 4～15MPa.
Low pressure sealed reservoir is enclosed gas charging fuel tank, and the operating pressure of low pressure sealed reservoir is 0.5～3MPa.
Hydraulic control unit integrated installation has the first one way valve, the second one way valve, the 3rd one way valve, the first safety valve, the second safety valve, the 3rd safety valve, the first pressure sensor, the second pressure sensor, the first solenoid operated directional valve, the second solenoid operated directional valve, the 3rd solenoid operated directional valve, the first solenoid-operated proportional reversal valve, the second solenoid-operated proportional reversal valve, the 3rd solenoid-operated proportional reversal valve and the 4th solenoid-operated proportional reversal valve, the first pressure sensor and the second pressure sensor, hydraulic control unit is provided with inner oil duct, hydraulic control unit is also provided with the hydraulic fluid port 6a being connected with outside oil circuit, hydraulic fluid port 6b, hydraulic fluid port 6c, hydraulic fluid port 6d, hydraulic fluid port 6e, hydraulic fluid port 6f, hydraulic fluid port 6g, hydraulic fluid port 6h, hydraulic fluid port 6i, hydraulic fluid port 6j,
The first solenoid operated directional valve, the second solenoid operated directional valve, the 3rd solenoid operated directional valve are bi-bit bi-pass solenoid operated directional valves, and the first solenoid-operated proportional reversal valve, the second solenoid-operated proportional reversal valve, the 3rd solenoid-operated proportional reversal valve and the 4th solenoid-operated proportional reversal valve are all two-position four-way solenoid-operated proportional reversal valves.
The P1 hydraulic fluid port of the first solenoid operated directional valve is by the inside oil duct of hydraulic control unit and the P2 oil-in of the first one way valve, the 6a hydraulic fluid port of hydraulic control unit is interconnected, the T1 hydraulic fluid port of the first solenoid operated directional valve is by the inside oil duct of hydraulic control unit and the 6b hydraulic fluid port of hydraulic control unit, the T14 oil-out of the first safety valve, the T12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve, the T4 hydraulic fluid port of the first solenoid-operated proportional reversal valve, the T11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve, the T5 hydraulic fluid port of the second solenoid-operated proportional reversal valve, the T10 oil-out of the second safety valve, the P9 oil-in of the second one way valve, the T8 oil-out of the 3rd safety valve, the P7 oil-in of the 3rd one way valve is interconnected,
The T2 oil-out of the first one way valve is interconnected by the inside oil duct of hydraulic control unit and the P3 hydraulic fluid port of the second solenoid operated directional valve, the P13 hydraulic fluid port of the 3rd solenoid operated directional valve, the P14 hydraulic fluid port of the first safety valve;
The T3 hydraulic fluid port of the second solenoid operated directional valve is interconnected by the inside oil duct of hydraulic control unit and the P4 hydraulic fluid port of the first solenoid-operated proportional reversal valve, the P11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve, the 6g hydraulic fluid port of hydraulic control unit, the 6h hydraulic fluid port of hydraulic control unit;
The T13 hydraulic fluid port of the 3rd solenoid operated directional valve is interconnected by the inside oil duct of hydraulic control unit and the P12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve, the P5 hydraulic fluid port of the second solenoid-operated proportional reversal valve, the 6e hydraulic fluid port of hydraulic control unit, the 6f hydraulic fluid port of hydraulic control unit;
The A4 hydraulic fluid port of the first solenoid-operated proportional reversal valve is communicated with by the inside oil duct of hydraulic control unit and the B5 hydraulic fluid port of the second solenoid-operated proportional reversal valve, the 6j hydraulic fluid port of hydraulic control unit, and the B4 hydraulic fluid port of the first solenoid-operated proportional reversal valve is interconnected by the inside oil duct of hydraulic control unit and the A5 hydraulic fluid port of the second solenoid-operated proportional reversal valve, the 6i hydraulic fluid port of hydraulic control unit;
The A12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve is interconnected by the inside oil duct of hydraulic control unit and the B11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve, the P8 oil-in of the 3rd safety valve, the T7 oil-out of the 3rd one way valve, the 6c hydraulic fluid port of hydraulic control unit, and the B12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve is interconnected by the inside oil duct of hydraulic control unit and the A11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve, the P10 hydraulic fluid port of the second safety valve, the T9 oil-out of the second one way valve, the 6d hydraulic fluid port of hydraulic control unit;
The 6a hydraulic fluid port of hydraulic control unit is communicated with the oil-out of hydraulic pump by fluid pressure line, the 6b hydraulic fluid port of hydraulic control unit is communicated with the oil return opening of low pressure sealed reservoir by fluid pressure line, the 6c hydraulic fluid port of hydraulic control unit is communicated with the loculus of rotary ink tank by fluid pressure line, the 6d hydraulic fluid port of hydraulic control unit is communicated with the large chamber of rotary ink tank by fluid pressure line, the 6e hydraulic fluid port of hydraulic control unit is communicated with the signal detecting mouth of second pressure sensor, the 6f hydraulic fluid port of hydraulic control unit is communicated with intermediate-pressure accumulator by fluid pressure line, the 6g hydraulic fluid port of hydraulic control unit is communicated with the signal detecting mouth of first pressure sensor, the 6h hydraulic fluid port of hydraulic control unit is communicated with high pressure accumulator by fluid pressure line, the 6i hydraulic fluid port of hydraulic control unit is communicated with the loculus of boom cylinder by fluid pressure line, the 6j hydraulic fluid port of hydraulic control unit is communicated with the large chamber of boom cylinder by fluid pressure line.
The oil-in of hydraulic pump is communicated with the oil-out of oil filter by fluid pressure line, and the oil-in of oil filter is communicated with the oil-out of low pressure sealed reservoir by fluid pressure line.
The present invention compared with prior art, its advantage is: utilize high pressure accumulator and intermediate-pressure accumulator to store the excess energy of loader under running on the lower load, in swing arm decline and rotating bucket discharge process, reclaim the potential energy of swing arm decline and rotating bucket discharging, turn over journey on swing arm rising, rotating bucket in, driven by hydraulic pump and high pressure accumulator interflow, improve the work operations efficiency of loader; Turn over journey under swing arm decline, rotating bucket in, provide working hydraulic pressure by intermediate-pressure accumulator, can reduce like this engine consumption, improve the operating efficiency of loader; In mechanical loader braking process, reclaim load mechanism energy and be stored in high pressure accumulator; In the time of loader loading operation intermittence and forward gear deadhead operation, the hydraulic energy of the generation of Engine driven Hydraulic Pump is stored in intermediate-pressure accumulator, and reach after the highest accumulation of energy pressure of setting at high pressure accumulator, intermediate-pressure accumulator, by the first solenoid operated directional valve to hydraulic pump off-load.Can reduce like this fuel oil oil consumption of loader, improve the operating efficiency of loader.
Brief description of the drawings
Fig. 1 is existing loader hydraulic system figure.
Fig. 2 is the loader hydraulic system figure of the embodiment of the present invention.
In figure: 1. the first solenoid operated directional valve, 2. the first one way valve, 3. the second solenoid operated directional valve, 4. the first solenoid-operated proportional reversal valve, 5. the second solenoid-operated proportional reversal valve, 6. hydraulic control unit, 7. the 3rd one way valve, 8. the 3rd safety valve, 9. the second one way valve, 10. the second safety valve, 11. the 3rd solenoid-operated proportional reversal valves, 12. the 4th solenoid-operated proportional reversal valves, 13. the 3rd solenoid operated directional valves, 14. first safety valves, 15. boom cylinders, 16. high pressure accumulators, 17. first pressure sensors, 18. intermediate-pressure accumulators, 19. second pressure sensors, 20. rotary ink tanks, 21. low pressure sealed reservoirs, 22. oil filters, 23. hydraulic pumps, 24. open type oil tanks, 25. rotating bucket connection guiding valves, 26. swing arm connection guiding valves.
Detailed description of the invention
Describe the present invention below in conjunction with drawings and Examples.
Fig. 1 is existing loader hydraulic system, comprises that hydraulic pump 23, boom cylinder 15, rotary ink tank 20, the first safety valve 14, oil filter 22, rotating bucket manually join guiding valve 25, swing arm and manually join guiding valve 26, the second one way valve 9, the second safety valve 10, the 3rd one way valve 7, the 3rd safety valve 8 and open type oil tank 24.When loader work, hydraulic pump 23 is turned round by motor driven, manually join guiding valve 25 and control rotary ink tank 20 work and realize rotating bucket shovel material, discharging by handling rotating bucket, manually join guiding valve 26 and realize lifting, the decline of controlling boom cylinders 15 work and realize swing arm by handling swing arm.In the time of loader loading operation, lifting, the decline of rotating bucket shovel material, discharging and swing arm relies on Engine driven Hydraulic Pump running to carry out work completely, the potential energy in swing arm decline process can not be recycled, the kinetic energy in the braking procedure of loader can not be recycled.
The loader hydraulic system of the embodiment of the present invention shown in Fig. 2, comprise hydraulic pump 23, low pressure sealed reservoir 21, high pressure accumulator 16, intermediate-pressure accumulator 18, hydraulic control unit 6, boom cylinder 15, rotary ink tank 20, oil filter 23, wherein hydraulic control unit 6 integrated installations have the first solenoid operated directional valve 1, the second solenoid operated directional valve 3, the 3rd solenoid operated directional valve 13, the first solenoid-operated proportional reversal valve 4, the second solenoid-operated proportional reversal valve 5, the 3rd solenoid-operated proportional reversal valve 11, the 4th solenoid-operated proportional reversal valve 12, the first one way valve 2, the second one way valve 9, the 3rd one way valve 7, the first safety valve 14, the second safety valve 10, the 3rd safety valve 8, the first pressure sensor 17, the second pressure sensor 19, hydraulic control unit 6 is provided with inner oil duct, hydraulic control unit 6 is also provided with the hydraulic fluid port 6a being connected with outside oil circuit, hydraulic fluid port 6b, hydraulic fluid port 6c, hydraulic fluid port 6d, hydraulic fluid port 6e, hydraulic fluid port 6f, hydraulic fluid port 6g, hydraulic fluid port 6h, hydraulic fluid port 6i, hydraulic fluid port 6j,
High pressure accumulator 16 adopts piston accumulator, and the operating pressure of high pressure accumulator 16 is 18～31.5MPa, the maximum working pressure P of high pressure accumulator 16
high max=31.5MPa, its operating pressure detects by the first pressure sensor 17;
Intermediate-pressure accumulator 18 adopts bladder accumulator, and the operating pressure of intermediate-pressure accumulator 18 is 5～12MPa, the maximum working pressure P of intermediate-pressure accumulator 18
middle max=12MPa, its operating pressure detects by the second pressure sensor 19;
Low pressure sealed reservoir 21 adopts enclosed gas charging fuel tank, and the operating pressure of low pressure sealed reservoir is 0.5～2.5MPa;
The effect of the first safety valve 14 is the maximum working pressures that limit hydraulic pump, and its maximum working pressure is 31.5MPa;
The effect of the second safety valve 10 is: prevent the impact of rotating bucket external load in loading operation process, limit the maximum working pressure in rotary ink tank 20 large chambeies;
The effect of the 3rd safety valve 8 is: prevent the impact of rotating bucket external load in loading operation process, limit the maximum working pressure of rotary ink tank 20 loculuses;
The effect of the first one way valve 2 is to prevent from flowing backwards to hydraulic pump 23 from the fluid of high pressure accumulator 16 and intermediate-pressure accumulator 18;
The effect of the second one way valve 9 is: in swing arm lifting process when moved arm lifting is when a certain position, the piston rod of rotary ink tank 20 pulls out, the loculus pressure of rotary ink tank 20 is raise, the little cavity pressure of rotary ink tank 20 carries out pressure release by the second safety valve, and the second one way valve repairing can be passed through in the large chamber of rotary ink tank 20, to eliminate the large chamber vacuum of rotary ink tank 20;
The effect of the 3rd one way valve 7 is: in the time of rotary ink tank 20 discharging, the cavity of resorption repairing to rotary ink tank 20 fast after scraper bowl is crossed lower twisted point, clashes into limited block and realize scraper bowl discharging;
The first solenoid operated directional valve 1 is bi-bit bi-pass solenoid operated directional valve, for the off-load control of hydraulic pump 23;
The second solenoid operated directional valve 3 is bi-bit bi-pass solenoid operated directional valves, for the accumulation of energy control of high pressure accumulator 16 and the supply control of working solution force feed;
The 3rd solenoid operated directional valve 13 is bi-bit bi-pass solenoid operated directional valves, presses the accumulation of energy control of accumulator 18 for pressure;
The first solenoid-operated proportional reversal valve 4 is two-position four-way solenoid-operated proportional reversal valves, for the lifting control of boom cylinder 15;
The second solenoid-operated proportional reversal valve 5 is two-position four-way solenoid-operated proportional reversal valves, for the decline control of boom cylinder 15;
The 3rd solenoid-operated proportional reversal valve 11 is two-position four-way solenoid-operated proportional reversal valves, for the shovel material control of pivoted arm arm oil cylinder 20;
The 4th solenoid-operated proportional reversal valve 12 is two-position four-way solenoid-operated proportional reversal valves, for the discharging control of pivoted arm arm oil cylinder 20;
The P1 hydraulic fluid port of the first solenoid operated directional valve 1 is by the inside oil duct of hydraulic control unit 6 and the P2 oil-in of the first one way valve 2, the 6a hydraulic fluid port of hydraulic control unit 6 is interconnected, the T1 hydraulic fluid port of the first solenoid operated directional valve 1 is by the inside oil duct of hydraulic control unit 6 and the 6b hydraulic fluid port of hydraulic control unit 6, the T14 oil-out of the first safety valve 14, the T12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve 12, the T4 hydraulic fluid port of the first solenoid-operated proportional reversal valve 4, the T11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve 11, the T5 hydraulic fluid port of the second solenoid-operated proportional reversal valve 5, the T10 hydraulic fluid port of the second safety valve 10, the P9 hydraulic fluid port of the second one way valve 9, the T8 hydraulic fluid port of the 3rd safety valve 8, the P7 hydraulic fluid port of the 3rd one way valve 7 is interconnected,
The T2 hydraulic fluid port of the first one way valve 2 is interconnected by the inside oil duct of hydraulic control unit 6 and the P3 hydraulic fluid port of the second solenoid operated directional valve 3, the P13 hydraulic fluid port of the 3rd solenoid operated directional valve 13, the P14 hydraulic fluid port of the first safety valve 14;
The T3 hydraulic fluid port of the second solenoid operated directional valve 3 is interconnected by the inside oil duct of hydraulic control unit 6 and the P4 hydraulic fluid port of the first solenoid-operated proportional reversal valve 4, the P11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve 11, the 6g hydraulic fluid port of hydraulic control unit 6, the 6h hydraulic fluid port of hydraulic control unit 6;
The T13 hydraulic fluid port of the 3rd solenoid operated directional valve 13 is interconnected by the inside oil duct of hydraulic control unit 6 and the P12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve 12, the P5 hydraulic fluid port of the second solenoid-operated proportional reversal valve 5, the 6e hydraulic fluid port of hydraulic control unit 6, the 6f hydraulic fluid port of hydraulic control unit 6;
The A4 hydraulic fluid port of the first solenoid-operated proportional reversal valve 4 is communicated with by the inside oil duct of hydraulic control unit 6 and the B5 hydraulic fluid port of the second solenoid-operated proportional reversal valve 5, the 6j hydraulic fluid port of hydraulic control unit 6, and the B4 hydraulic fluid port of the first solenoid-operated proportional reversal valve 4 is interconnected by the inside oil duct of hydraulic control unit 6 and the A5 hydraulic fluid port of the second solenoid-operated proportional reversal valve 5, the 6i hydraulic fluid port of hydraulic control unit 6;
The A12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve 12 is interconnected by the inside oil duct of hydraulic control unit 6 and the B11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve 11, the P8 oil-in of the 3rd safety valve 8, the T7 oil-out of the 3rd one way valve 7, the 6c hydraulic fluid port of hydraulic control unit 6, and the B12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve 12 is interconnected by the inside oil duct of hydraulic control unit 6 and the A11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve 11, the P10 hydraulic fluid port of the second safety valve 10, the T9 oil-out of the second one way valve 9, the 6d hydraulic fluid port of hydraulic control unit 6;
The 6a hydraulic fluid port of hydraulic control unit 6 is communicated with the oil-out of hydraulic pump 23 by fluid pressure line, the 6b hydraulic fluid port of hydraulic control unit 6 is communicated with the oil return opening of low pressure sealed reservoir 21 by fluid pressure line, the 6c hydraulic fluid port of hydraulic control unit 6 is communicated with the loculus of rotary ink tank 20 by fluid pressure line, the 6d hydraulic fluid port of hydraulic control unit 6 is communicated with the large chamber of rotary ink tank 20 by fluid pressure line, the 6e hydraulic fluid port of hydraulic control unit 6 is communicated with the signal detecting mouth of second pressure sensor 21, the 6f hydraulic fluid port of hydraulic control unit 6 is communicated with intermediate-pressure accumulator 18, the 6g hydraulic fluid port of hydraulic control unit 6 is communicated with the signal detecting mouth of first pressure sensor 17, the 6h hydraulic fluid port of hydraulic control unit 6 is communicated with high pressure accumulator 16 by fluid pressure line, the 6i hydraulic fluid port of hydraulic control unit 6 is communicated with the loculus of boom cylinder 15 by fluid pressure line, the 6j hydraulic fluid port of hydraulic control unit 6 is communicated with the large chamber of boom cylinder 15 by fluid pressure line.
The oil-in of hydraulic pump 23 is communicated with the oil-out of oil filter 22 by fluid pressure line, and the oil-in of oil filter 22 is communicated with the oil-out of low pressure sealed reservoir 21 by fluid pressure line.
The course of work of the loader hydraulic system to this inventive embodiments is further described below:
The course of work of moved arm lifting is: control the size that the electromagnet of the first solenoid-operated proportional reversal valve 4 is switched on and regulated its electrical current, after the electromagnet energising of the first solenoid-operated proportional reversal valve 4, high pressure liquid force feed flows out from high pressure accumulator 16, successively by the 6h hydraulic fluid port of hydraulic control unit 6, the P4 hydraulic fluid port of the first solenoid-operated proportional reversal valve 4, A4 hydraulic fluid port, the inside oil duct of hydraulic control unit 6, the 6j hydraulic fluid port of hydraulic control unit 6, enter the large chamber of boom cylinder 15 through fluid pressure line, make moved arm lifting, moved arm lifting speed can regulate by the electrical current size that changes the first solenoid-operated proportional reversal valve 4, and the fluid of boom cylinder 15 loculuses is under the effect of oil cylinder piston, successively by the 6i hydraulic fluid port of hydraulic control unit 6, the B4 hydraulic fluid port of the first solenoid-operated proportional reversal valve 4, T4 hydraulic fluid port, the 6b hydraulic fluid port of hydraulic control unit 6, enter low pressure sealed reservoir 21 through fluid pressure line, meanwhile, the electromagnet energising of the second solenoid operated directional valve 3, after the electromagnet energising of the second solenoid operated directional valve 3, from the high pressure liquid force feed of hydraulic pump 23 after 3 P3 of one way valve 2, the second solenoid operated directional valve, T3 hydraulic fluid port, with the high pressure liquid force feed interflow of flowing out from high pressure accumulator 16, enter the large chamber of boom cylinder 15 by P4, the A4 hydraulic fluid port of the first solenoid-operated proportional reversal valve 4, make in moved arm lifting process in the situation that not increasing engine load and hydraulic pump 23 rotating speed, accelerate moved arm lifting speed.
The course of work that swing arm declines is: control the size that the electromagnet of the second solenoid-operated proportional reversal valve 5 is switched on and regulated its electrical current, after the electromagnet energising of the second solenoid-operated proportional reversal valve 5, middle hydraulic fluid force feed flows out from intermediate-pressure accumulator 18, pass through successively the 6f hydraulic fluid port of hydraulic control unit 6, the P5 of the second solenoid-operated proportional reversal valve 5, A5 hydraulic fluid port enters boom cylinder 15 loculuses, swing arm is declined, swing arm decrease speed can be by changing the second solenoid-operated proportional reversal valve 5 the size of electromagnet electrical current regulate, and the fluid in boom cylinder 15 large chambeies is under the effect of oil cylinder piston, pass through successively the 6j hydraulic fluid port of hydraulic control unit 6, the B5 hydraulic fluid port of the second solenoid-operated proportional reversal valve 5, T5 hydraulic fluid port, after the 6b hydraulic fluid port of hydraulic control unit 6, enter low pressure sealed reservoir 21 through fluid pressure line, due in swing arm decline process, the fluid in boom cylinder 15 large chambeies, after the B5 hydraulic fluid port and T5 hydraulic fluid port of the second solenoid-operated proportional reversal valve 5, enter low pressure sealed reservoir 21, and low pressure sealed reservoir 21 is enclosed air tanks, the blowing pressure of low pressure sealed reservoir 21 is raise, thereby the gravitional force in swing arm decline process can be stored in low pressure sealed reservoir 21 in the mode of gas pressure potential energy.Meanwhile, the second solenoid operated directional valve 3 is switched on, high pressure liquid force feed from hydraulic pump 23 enters high pressure accumulator 16 through P3, the T3 hydraulic fluid port of one way valve 2, the second solenoid operated directional valve 3, the high pressure liquid force feed that hydraulic pump 23 is produced is stored in high pressure accumulator 16, to store the energy of motor and hydraulic pump.Like this, not only the gravitional force in swing arm decline process can be reclaimed and is stored in low pressure sealed reservoir 21, and can be by the energy storage in motor and hydraulic pump 23 operation process in high pressure accumulator 16.
The course of work turning on rotating bucket is: control the electromagnetic valve Tie Tong electricity of the 3rd solenoid-operated proportional reversal valve 11 and regulate the size of its electrical current, after the electromagnetic valve Tie Tong electricity of the 3rd solenoid-operated proportional reversal valve 11, high pressure liquid force feed flows out from high pressure accumulator 16, pass through successively the 6h hydraulic fluid port of hydraulic control unit 6, the P11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve 11, A11 hydraulic fluid port enters the large chamber of rotary ink tank 20, make to turn on rotating bucket, the speed turning on rotating bucket can regulate by the electromagnet electrical current that changes the 3rd solenoid-operated proportional reversal valve 11, and the fluid of rotary ink tank 20 loculuses is under the effect of oil cylinder piston, successively by the 6c hydraulic fluid port of hydraulic control unit 6, the B11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve 11, T11 hydraulic fluid port, the 6b hydraulic fluid port of hydraulic control unit 6 enters low pressure sealed reservoir 21, meanwhile, control the electromagnet energising of the second solenoid operated directional valve 3, when after the electromagnet energising of the second solenoid operated directional valve 3, from the high pressure liquid force feed of hydraulic pump 23 through one way valve 2, the P3 hydraulic fluid port of the second solenoid operated directional valve 3, T3 hydraulic fluid port, enter the large chamber of rotary ink tank 20 with the high pressure liquid force feed interflow of flowing out from high pressure accumulator 16, making to turn over Cheng Zhong on rotating bucket does not increase in the situation of engine load, accelerates rotary speed on rotating bucket.
The course of work turning under rotating bucket is: control the size that the electromagnet of the 4th solenoid-operated proportional reversal valve 12 is switched on and regulated its electrical current, after the electromagnet energising of the 4th solenoid-operated proportional reversal valve 12, middle hydraulic fluid force feed flows out from intermediate-pressure accumulator 18, successively by the 6f hydraulic fluid port of hydraulic control unit 6, the P12 of the 4th solenoid-operated proportional reversal valve 12, A12 hydraulic fluid port, the 6c hydraulic fluid port of hydraulic control unit 6, enter the loculus of rotary ink tank 20 through fluid pressure line, make unloading material under rotating bucket, and the fluid in rotary ink tank 20 large chambeies is under the effect of oil cylinder piston, successively by the 6d hydraulic fluid port of hydraulic control unit 6, the B12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve 12, T12 hydraulic fluid port, after the 6b hydraulic fluid port of hydraulic control unit 6, enter low pressure sealed reservoir 21, because low pressure sealed reservoir 21 is enclosed air tanks, in the process turning under rotating bucket, make the blowing pressure of low pressure sealed reservoir 21 raise, thereby the gravitional force turning under rotating bucket in journey can be stored in low pressure sealed reservoir 21 in the mode of gas pressure potential energy, meanwhile, the second solenoid operated directional valve 3 is switched on, high pressure liquid force feed from hydraulic pump 23 enters high pressure accumulator 16 through P3, the T3 hydraulic fluid port of one way valve 2, the second solenoid operated directional valve 3, the high pressure liquid force feed that hydraulic pump 23 is produced is stored in high pressure accumulator 18, to store the energy of motor and hydraulic pump.Like this, not only the gravitional force recovery turning under rotating bucket in journey can be stored in low pressure sealed reservoir 21, and can be by the energy storage in motor and hydraulic pump 23 operation process in high pressure accumulator 18.
The course of work of intermediate-pressure accumulator 18 accumulation of energys is: in loader loading operation intermittently and when forward gear deadhead operation, the pressure detecting when the second pressure sensor 19 is less than the maximum working pressure P of intermediate-pressure accumulator 18
middle maxwhen=12MPa, control the electromagnet energising of the 3rd solenoid operated directional valve 13, after the electromagnet energising of the 3rd solenoid operated directional valve 13, hydraulic oil pumps from the oil-out of hydraulic pump 23, enter intermediate-pressure accumulator 18 through P13 and the T12 hydraulic fluid port of one way valve 2, the 3rd solenoid operated directional valve 13 successively, the pressure of intermediate-pressure accumulator 18 is raise, pressure store energy in intermediate-pressure accumulator 18.
The course of work that braking energy reclaims is: in the time of mechanical loader braking, control the electromagnet energising of the second solenoid operated directional valve 3, after the electromagnet energising of the second solenoid operated directional valve 3, hydraulic oil pumps from the oil-out of hydraulic pump 23, P3 and T3 hydraulic fluid port through one way valve 2, the second solenoid operated directional valve 3 enter high pressure accumulator 18, the pressure of high pressure accumulator 18 is raise, and is that air pressure potential energy is stored in high pressure accumulator 18 by the kinetic transformation of loader; When the detected pressures of the first pressure sensor 17 equals the maximum working pressure P of high pressure accumulator 16
high maxthe pressure that=31.5MPa and the second pressure sensor 19 detect is less than the maximum working pressure P of intermediate-pressure accumulator 18
middle maxwhen=12MPa, control the electromagnet energising of the 3rd solenoid operated directional valve 13, after the electromagnet energising of the 3rd solenoid operated directional valve 13, hydraulic oil flows out from the oil-out of hydraulic pump 23, enter intermediate-pressure accumulator 18 through the first one way valve 2, the P13 hydraulic fluid port of the 3rd solenoid operated directional valve 13, T13 hydraulic fluid port successively, part braking energy is stored in intermediate-pressure accumulator 18.
The course of work of hydraulic pump off-load is: when the detected pressures of the first pressure sensor 17 equals the maximum working pressure P of accumulator 16
high maxthe pressure that=31.5MPa and the second pressure sensor 19 detect equals the maximum working pressure P of intermediate-pressure accumulator 18
middle maxwhen=12MPa, control the electromagnetic valve energising of the first solenoid operated directional valve 1, the hydraulic oil that hydraulic pump 23 pumps, through P1 hydraulic fluid port, T1 hydraulic fluid port, the oil duct of hydraulic control unit 6, the 6b hydraulic fluid port of the first solenoid operated directional valve 1, through fluid pressure line low pressure sealed reservoir 21, makes hydraulic pump 23 off-loads.
By reference to the accompanying drawings embodiments of the present invention are explained in detail above, but the present invention is not limited to above-mentioned embodiment, in the ken possessing at affiliated technical field those of ordinary skill, can also under the prerequisite that does not depart from aim of the present invention, make various variations.
Claims (14)
1. a loader hydraulic system, comprise hydraulic pump (23), low pressure sealed reservoir (21), high pressure accumulator (16), intermediate-pressure accumulator (18), hydraulic control unit (6), boom cylinder (15), rotary ink tank (20), oil filter (22), it is characterized in that:
Described hydraulic control unit (6) integrated installation has the first one way valve (2), the second one way valve (9), the 3rd one way valve (7), the first safety valve (14), the second safety valve (10), the 3rd safety valve (8), the first pressure sensor (17), the second pressure sensor (19), the first solenoid operated directional valve (1), the second solenoid operated directional valve (3), the 3rd solenoid operated directional valve (13), the first solenoid-operated proportional reversal valve (4), the second solenoid-operated proportional reversal valve (5), the 3rd solenoid-operated proportional reversal valve (11) and the 4th solenoid-operated proportional reversal valve (12), hydraulic control unit (6) is provided with inner oil duct, and hydraulic control unit (6) is also provided with the hydraulic fluid port 6a being connected with outside oil circuit, hydraulic fluid port 6b, hydraulic fluid port 6c, hydraulic fluid port 6d, hydraulic fluid port 6e, hydraulic fluid port 6f, hydraulic fluid port 6g, hydraulic fluid port 6h, hydraulic fluid port 6i, hydraulic fluid port 6j,
The P1 hydraulic fluid port of described the first solenoid operated directional valve (1) is by the inside oil duct of hydraulic control unit (6) and the P2 oil-in of the first one way valve (2), the 6a hydraulic fluid port of hydraulic control unit (6) is interconnected, the T1 hydraulic fluid port of the first solenoid operated directional valve (1) is by the inside oil duct of hydraulic control unit (6) and the 6b hydraulic fluid port of hydraulic control unit (6), the T14 oil-out of the first safety valve (14), the T12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve (12), the T4 hydraulic fluid port of the first solenoid-operated proportional reversal valve (4), the T11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve (11), the T5 hydraulic fluid port of the second solenoid-operated proportional reversal valve (5), the T10 oil-out of the second safety valve (10), the P9 oil-in of the second one way valve (9), the T8 oil-out of the 3rd safety valve (8), the P7 oil-in of the 3rd one way valve (7) is interconnected,
The T2 oil-out of described the first one way valve (2) is interconnected by the inside oil duct of hydraulic control unit (6) and the P3 hydraulic fluid port of the second solenoid operated directional valve (3), the P13 hydraulic fluid port of the 3rd solenoid operated directional valve (13), the P14 hydraulic fluid port of the first safety valve (14);
The T3 hydraulic fluid port of described the second solenoid operated directional valve (3) is interconnected by the inside oil duct of hydraulic control unit (6) and the P4 hydraulic fluid port of the first solenoid-operated proportional reversal valve (4), the P11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve (11), the 6g hydraulic fluid port of hydraulic control unit (6), the 6h hydraulic fluid port of hydraulic control unit (6);
The T13 hydraulic fluid port of described the 3rd solenoid operated directional valve (13) is interconnected by the inside oil duct of hydraulic control unit (6) and the P12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve (12), the P5 hydraulic fluid port of the second solenoid-operated proportional reversal valve (5), the 6e hydraulic fluid port of hydraulic control unit (6), the 6f hydraulic fluid port of hydraulic control unit (6);
The A4 hydraulic fluid port of described the first solenoid-operated proportional reversal valve (4) is communicated with by the 6j hydraulic fluid port of the inside oil duct of hydraulic control unit (6) and the B5 hydraulic fluid port of the second solenoid-operated proportional reversal valve (5), hydraulic control unit (6), and the B4 hydraulic fluid port of the first solenoid-operated proportional reversal valve (4) is interconnected by the 6i hydraulic fluid port of the inside oil duct of hydraulic control unit (6) and the A5 hydraulic fluid port of the second solenoid-operated proportional reversal valve (5), hydraulic control unit (6);
The A12 hydraulic fluid port of described the 4th solenoid-operated proportional reversal valve (12) is by the inside oil duct of hydraulic control unit (6) and the B11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve (11), the P8 oil-in of the 3rd safety valve (8), the T7 oil-out of the 3rd one way valve (7), the 6c hydraulic fluid port of hydraulic control unit (6) is communicated with, the B12 hydraulic fluid port of the 4th solenoid-operated proportional reversal valve (12) is by the inside oil duct of hydraulic control unit (6) and the A11 hydraulic fluid port of the 3rd solenoid-operated proportional reversal valve (11), the P10 hydraulic fluid port of the second safety valve (10), the T9 oil-out of the second one way valve (9), the 6d hydraulic fluid port of hydraulic control unit (6) is interconnected,
The 6a hydraulic fluid port of described hydraulic control unit (6) is communicated with the oil-out of hydraulic pump (23) by fluid pressure line, the 6b hydraulic fluid port of hydraulic control unit (6) is communicated with the oil return opening of low pressure sealed reservoir (21) by fluid pressure line, the 6c hydraulic fluid port of hydraulic control unit (6) is communicated with the loculus of rotary ink tank (20) by fluid pressure line, the 6d hydraulic fluid port of hydraulic control unit (6) is communicated with the large chamber of rotary ink tank (20) by fluid pressure line, the 6e hydraulic fluid port of hydraulic control unit (6) is communicated with the signal detecting mouth of second pressure sensor (19), the 6f hydraulic fluid port of hydraulic control unit (6) is communicated with intermediate-pressure accumulator (18), the 6g hydraulic fluid port of hydraulic control unit (6) is communicated with the signal detecting mouth of first pressure sensor (17), the 6h hydraulic fluid port of hydraulic control unit (6) is communicated with high pressure accumulator (16) by fluid pressure line, the 6i hydraulic fluid port of hydraulic control unit (6) is communicated with the loculus of boom cylinder (15) by fluid pressure line, the 6j hydraulic fluid port of hydraulic control unit (6) is communicated with the large chamber of boom cylinder (15) by fluid pressure line.
2. loader hydraulic system as claimed in claim 1, is characterized in that: described high pressure accumulator (16) is piston type or bladder accumulator.
3. loader hydraulic system as claimed in claim 1, is characterized in that: described intermediate-pressure accumulator (18) is piston type or bladder accumulator.
4. loader hydraulic system as claimed in claim 1, is characterized in that: described low pressure sealed reservoir (21) is enclosed gas charging fuel tank.
5. loader hydraulic system as claimed in claim 1, is characterized in that: described the first solenoid operated directional valve (1) is bi-bit bi-pass solenoid operated directional valve.
6. loader hydraulic system as claimed in claim 1, is characterized in that: described the second solenoid operated directional valve (3) is bi-bit bi-pass solenoid operated directional valve.
7. loader hydraulic system as claimed in claim 1, is characterized in that: described the 3rd solenoid operated directional valve (13) is bi-bit bi-pass solenoid operated directional valve.
8. loader hydraulic system as claimed in claim 1, is characterized in that: described the first solenoid-operated proportional reversal valve (4) is two-position four-way solenoid-operated proportional reversal valve.
9. loader hydraulic system as claimed in claim 1, is characterized in that: described the second solenoid-operated proportional reversal valve (5) is two-position four-way solenoid-operated proportional reversal valve.
10. loader hydraulic system as claimed in claim 1, is characterized in that: described the 3rd solenoid-operated proportional reversal valve (11) is two-position four-way solenoid-operated proportional reversal valve.
11. loader hydraulic systems as claimed in claim 1, is characterized in that: described the 4th solenoid-operated proportional reversal valve (12) is two-position four-way solenoid-operated proportional reversal valve.
12. loader hydraulic systems as claimed in claim 1, is characterized in that: the operating pressure of described high pressure accumulator (16) is 16～35MPa.
13. loader hydraulic systems as claimed in claim 1, is characterized in that: the operating pressure of described intermediate-pressure accumulator (18) is 4～15MPa.
14. loader hydraulic systems as claimed in claim 1, is characterized in that: the operating pressure of described low pressure sealed reservoir (21) is 0.5～3 MPa.
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| CN201210135603.3A CN102635144B (en) | 2012-05-04 | 2012-05-04 | Hydraulic system for loader |
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| CN201210135603.3A CN102635144B (en) | 2012-05-04 | 2012-05-04 | Hydraulic system for loader |
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| CN102635144B true CN102635144B (en) | 2014-06-11 |
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| DE102015116763A1 (en) * | 2015-10-02 | 2017-04-06 | Linde Hydraulics Gmbh & Co. Kg | Hydraulic constant pressure system |
| CN105178383B (en) * | 2015-10-19 | 2017-08-29 | 太原理工大学 | Load electromechanical drive independent steering system |
| CN107964992B (en) * | 2017-11-24 | 2023-03-17 | 山东临工工程机械有限公司 | Energy-saving hydraulic system of wood clamping fork loader |
| CN110182610B (en) * | 2019-04-29 | 2021-07-13 | 宝钢湛江钢铁有限公司 | Intelligent pitching hydraulic system of intelligent stacker-reclaimer and control method |
| CN111828411B (en) * | 2020-07-24 | 2022-03-01 | 中国人民解放军陆军装甲兵学院 | Hydraulic system based on two-stage energy supply and independent valve control of load port and control method |
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| CN1170831A (en) * | 1996-07-10 | 1998-01-21 | 三星重工业株式会社 | Hydraulic system for power loaders |
| US6434864B1 (en) * | 2000-09-22 | 2002-08-20 | Grigoriy Epshteyn | Frontal loader |
| JP2005155230A (en) * | 2003-11-27 | 2005-06-16 | Komatsu Ltd | Hydraulic circuit for suppressing traveling vibration of wheel type construction machine |
| CN101278130A (en) * | 2005-09-30 | 2008-10-01 | 卡特彼勒公司 | Hydraulic system for recovering potential energy |
| CN202544015U (en) * | 2012-05-04 | 2012-11-21 | 山东理工大学 | Hydraulic system of loader |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1170831A (en) * | 1996-07-10 | 1998-01-21 | 三星重工业株式会社 | Hydraulic system for power loaders |
| US6434864B1 (en) * | 2000-09-22 | 2002-08-20 | Grigoriy Epshteyn | Frontal loader |
| JP2005155230A (en) * | 2003-11-27 | 2005-06-16 | Komatsu Ltd | Hydraulic circuit for suppressing traveling vibration of wheel type construction machine |
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| CN202544015U (en) * | 2012-05-04 | 2012-11-21 | 山东理工大学 | Hydraulic system of loader |
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