CN101858368B - Multiple directional control valve system for return oil throttle control with load sensitive pressure compensation - Google Patents
Multiple directional control valve system for return oil throttle control with load sensitive pressure compensation Download PDFInfo
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Abstract
The invention relates to a multiple directional control valve system for return oil throttle control with load sensitive pressure compensation, in particular to a multiple directional control valve system apparatus for the return oil throttle control with load sensitive pressure compensation for excavators. In the system, a filter is communicated with a throttle valve communicated with a pressure reducing valve, the pressure reducing valve is communicated with a load sensor port, two ends of the control valve are respectively connected with a first control port or second control port, the load sensor port is communicated with a one-way valve communicated with a pressure compensator, and the pressure compensator is communicated with the control valve. The outlet of a load sensitive variable pump is respectively communicated with a flow control valve, a pressure stop valve, a power adjusting valve and a variable oil cylinder, the flow control valve is communicated with the variable oil cylinder and the load sensor port, and rod cavities of the first and second variable oil cylinder are respectively connected with a swash plate of the load sensitive variable pump. The invention has the advantages of simple structure, improved accuracy of operation, high control degree and reliability and is widely used for hydraulic multiple-way valve systems of the engineering machinery industry.
Description
Technical field
The present invention relates to a kind of multiple directional control valve system for return oil throttle control with load sensitive pressure compensation, particularly at the multiple directional control valve system for return oil throttle control with load sensitive pressure compensation equipment to excavator.
Background technique
At present, the assignment of traffic of open type hydraulic system is controlled and to be mostly the oil-feed of executive component is controlled, i.e. in addition throttling control and pressure compensation between executive component and delivery side of pump.Germany BOSCH-REXROTH company with pressure and the irrelevant assignment of traffic multi-way valve system of flow be comparatively advanced at present flow distributing system, even in the situation that the undercurrent amount can be accomplished with load irrelevant.But all there is a problem in all oil-feed control valves: under the effect of reverse load (driving direction that is final controlling element is identical with the load action direction), although compensator can accurately be controlled fuel supply flow rate, but in the situation that Fill valve is opened, the speed of final controlling element can exceed the control expected value, thereby the accuracy of impact operation, balance valve or uncompensated throttling is carried out in oil return is not opened Fill valve, but this can cause the extra pressure loss and cost to increase.
Summary of the invention
Purpose of the present invention, be to provide a kind of multiple directional control valve system for return oil throttle control with load sensitive pressure compensation, it is to adopt the oil return of final controlling element is controlled, and carry out load pressure compensation, overcome in prior art and can not accurately control, pressure loss rate is high, complex structure, the factor that cost is more high, realization accurately control and carry out the purpose of load pressure compensation to the oil return of final controlling element.
multiple directional control valve system for return oil throttle control with load sensitive pressure compensation of the present invention takes following technological scheme to realize: it is by being provided with load-transducing mouth and the load-reacting pump that pumps hydraulic fluid port, flow control valve, pressure shut-off valve, the power adjustments valve, the first variable oil cylinder, the second variable oil cylinder, swash plate, system's relief valve, leader unload valve, reduction valve, selector valve, the first one-way valve, the execution work oil cylinder, the second one-way valve, pressure compensator, the first overload valve, the second overload valve, filter, throttle valve and first is controlled mouth, second controls a mouthful composition, pumps hydraulic fluid port and system's relief valve, leader unload valve, the second one-way valve, filter is communicated with, system's relief valve, leader unload valve, selector valve, the first overload valve, the second overload valve is communicated with the system oil return mouth, and filter is communicated with throttle valve, and throttle valve is communicated with reduction valve, and reduction valve is communicated with the load-transducing mouth, and the second one-way valve is communicated with selector valve, selector valve, the first overload valve and the second overload valve are communicated with the execution work oil cylinder respectively, the selector valve two ends connect respectively first and control mouth or the second control mouth, the load-transducing mouth is communicated with one-way valve, and the first one-way valve is communicated with pressure compensator, and pressure compensator is communicated with selector valve.The load-reacting delivery side of pump is communicated with flow control valve, pressure shut-off valve, power adjustments valve, the first variable oil cylinder respectively, flow control valve is communicated with the second variable oil cylinder, flow control valve is communicated with the load-transducing mouth, the first variable oil cylinder be connected the rod chamber of variable oil cylinder and be connected with the swash plate of load-reacting pump respectively.
The first variable oil cylinder and the second variable oil cylinder are adjusted the flow of load-reacting pump by changing the swash plate pivot angle, when the oil pressure that acts on the second variable oil cylinder is higher, the swash plate pivot angle is less, and the flow output of load-reacting pump is also just fewer.The power adjustments valve is in right position under spring-force driven dual, the second variable oil cylinder working-pressure oil is by the oil return of power adjustments valve, and under oil pressure and spring action, swash plate swings to large direction of the traffic in the first variable oil cylinder chamber.In the first variable oil cylinder chamber, oil pressure acts on push rod, push rod promotes lever makes lever around a spot wobble, promoting the power adjustments valve moves right, make the power adjustments valve be in left position, the pressure oil of load-reacting pump enters the second variable oil cylinder by the power adjustments valve through pressure shut-off valve, promote its piston rod, overcome the first variable oil cylinder hydraulic power and Compress Spring swash plate is swung to the small flow direction.Because the first variable cylinder piston rod moves to right, the arm of force that push rod promotes lever reduces simultaneously, and the power that makes lever push away the power adjustments valve descends, until equate with power adjustments valve spring power, the swash plate pivot angle is in new equilibrium position, thereby realizes power control.
When the actuators such as multi-way valve manipulation swing arm, dipper, scraper bowl, soil-shifting; be the maximum locking pressure of restriction oil hydraulic cylinder under blocking; at two oil ports that connect actuator each first overload valve in parallel or second overload valve; set its maximum overload power; if surpass this pressure; the first overload valve and the second overload valve are opened, and unload, and have protected hydraulic element and pipeline to avoid damaging.Power shovel is when excavating; swing arm is inevitable stressed; in order to safeguard normal operation; although the swing arm oil hydraulic cylinder is located and " off position ", must there be enough large blocking force to resist and stretches and compression, this locking pressure is sometimes well beyond the maximum service pressure of system; when this locking pressure during greater than the overload valve set pressure; overload valve is opened, and working oil pressure release oil return is protected other hydraulic element and pipeline.
Multi-way valve mainly contains the three functions control valve: be respectively system's main safety valve, leader unload valve and load-sensitive reduction valve; System's relief valve is the Maximum operating pressure of controlling multi-way valve system, and leader unload valve is the leader unload valve with pilot stage, and pilot stage is subjected to compensatory pressure and guide's spring contrast control, and main valve is subjected to load-reacting pumping pressure and spring action.Selector valve is when meta, and each sheet reverse valve oil head is obstructed, and this moment, the load-sensitive compensatory pressure can be applied to the pilot stage of leader unload valve, leader unload valve was opened, the off-load of load-reacting pumping pressure; During selector valve work, the load-sensitive compensatory pressure can pass through the selector valve oil return unloading, the pilot valve of leader unload valve can not opened, the control oil pressure that acts on leader unload valve spring one end can not pressure release, so leader unload valve is in closed condition under the effect of load-reacting pumping pressure and spring.Each sheet of multi-way valve is when meta, load-reacting pump output services flow is by leader unload valve pressure release oil return, the load-reacting POF is very large, this moment, multi-way valve was at meta, each restriction is obstructed, and the load-sensitive compensatory pressure raises, and feeds back to the flow control valve of load-reacting pump, the force value that the load-sensitive compensatory pressure is set greater than the load-reacting pump is oil return pressure reduction, so the load-reacting pump duty reduces.During if any any a slice selector valve work, load-sensitive compensatory pressure oil can be through pressure compensator one-way valve pressure release oil return, load-sensitive compensatory pressure oil pressure reduces, feed back to the flow control valve of load-reacting pump, its load-reacting POF can be adjusted thereupon, in the time of selector valve stroke maximum, load-sensitive compensatory pressure oil is hardly through the direct pressure release oil return of throttling, this moment, load-sensitive compensatory pressure pressure was roughly zero, the load-reacting POF is maximum, and the load-reacting pump is controlled under curve at power and carried out Variable Control.The effect of load-sensitive compensatory pressure: as the stroking mechanism of feedback pressure signal feedback effect in the load-reacting pump, make the load-reacting POF adapt to all the time multi-way valve spool aperture needs, do not have unnecessary flow to run off, control to realize load-sensitive; Act on the oil circuit control of pressure compensator, control to realize pressure compensated flow.
The effect of multiple directional control valve system for return oil throttle control with load sensitive pressure compensation of the present invention is simple in structure, improve the accuracy of operation, control degree and reliability are high, can realize the soft control stably of hydraulic system full power, are widely used on the hydraulic multichannel valve system of construction machinery industry.
Description of drawings
Multiple directional control valve system for return oil throttle control with load sensitive pressure compensation of the present invention will be described in further detail with reference to Figs..
Accompanying drawing is multiple directional control valve system for return oil throttle control with load sensitive pressure compensation hydraulic control figure of the present invention.
1-load-reacting pump, 2-load-transducing mouth, 3-system overflow valve, 4-leader unload valve, 5-pressure-reducing valve 6-the first is controlled mouthful 7-reversal valve 8-the first check valve 9-oil cylinder 10-pressure compensator 11-the first overload valve the 12-the second overload valve 13-the second and is controlled mouthful 14-the second check valve 15-filter 16-choke valve 17-oil return opening 18-pump hydraulic fluid port 19-flow control valve 20-pressure shut-off valve 21-power adjusting valve 22-the first variable oil cylinder 23-swash plate the 24-the second variable oil cylinder.
Embodiment
with reference to accompanying drawing, multiple directional control valve system for return oil throttle control with load sensitive pressure compensation of the present invention, it is by being provided with load-transducing mouth 2 and the load-reacting pump 1 that pumps hydraulic fluid port 18, flow control valve 19, pressure shut-off valve 20, power adjustments valve 21, the first variable oil cylinder 22, the second variable oil cylinder 24, swash plate 23, system's relief valve 3, leader unload valve 4, reduction valve 5, selector valve 7, the first one-way valve 8, execution work oil cylinder 9, the second one-way valve 14, pressure compensator 10, the first overload valve 11, the second overload valve 12, filter 15, throttle valve 16 and first is controlled mouth 6, second controls mouthful 13 compositions, pumps hydraulic fluid port 18 and system's relief valve 3, leader unload valve 4, the second one-way valve 14, filter 15 is communicated with, system's relief valve 3, leader unload valve 4, selector valve 7, the first overload valve 11, the second overload valve 12 is communicated with system oil return mouth 17, and filter 15 is communicated with throttle valve 16, and throttle valve 16 is communicated with reduction valve 5, and reduction valve 5 is communicated with load-transducing mouth 2, and the second one-way valve 14 is communicated with selector valve 7, selector valve 7, the first overload valve 11 and the second overload valve 12 are communicated with execution work oil cylinder 9 respectively, and load-transducing mouth 2 is communicated with the first one-way valve 8, and the first one-way valve 8 is communicated with pressure compensator 10, and pressure compensator 10 is communicated with selector valve 7.The outlet of load-reacting pump 1 is communicated with flow control valve 19, pressure shut-off valve 20, power adjustments valve 21, the first variable oil cylinder 22 respectively, flow control valve 19 is communicated with the second variable oil cylinder 24, flow control valve 19 is communicated with load-transducing mouth 2, the first variable oil cylinder 22 be connected the rod chamber of variable oil cylinder 24 and be connected with the swash plate 23 of load-reacting pump 1 respectively.
Load-reacting pump 1 working principle: the first variable oil cylinder 22 and the second variable oil cylinder 24 are adjusted the flow of load-reacting pump 1 by changing swash plate 23 pivot angles, when the oil pressure that acts on the second variable oil cylinder 24 higher, swash plate 23 pivot angles are less, and the flow output of load-reacting pump 1 is also just fewer.Power adjustments valve 21 is in right position under spring-force driven dual, the second variable oil cylinder 24 pressure oils are by 21 oil returns of power adjustments valve, and under oil pressure and spring action, swash plate 23 swings to large direction of the traffic in the first variable oil cylinder 22 chambeies.In the first variable oil cylinder 22 chambeies, oil pressure acts on push rod, push rod promotes lever makes lever around a spot wobble, promoting power adjustments valve 21 moves right, make power adjustments valve 21 be in left position, the pressure oil of load-reacting pump 1 enters the second variable oil cylinder 24 by power adjustments valve 21 through pressure shut-off valve 20, promote its piston rod, overcome the first variable oil cylinder 22 hydraulic couplings and Compress Spring swash plate 23 is swung to the small flow direction.Simultaneously because the first variable oil cylinder 22 piston rods move to right, the arm of force that push rod promotes lever reduces, and the power that makes lever push away power adjustments valve 21 descends, until equate with power adjustments valve 21 spring forces, swash plate 23 pivot angles are in new equilibrium position, thereby realize power control.
The effect of the first overload valve 11 and the second overload valve 12: when the actuators such as multi-way valve manipulation swing arm, dipper, scraper bowl, soil-shifting; be the maximum locking pressure of restriction oil hydraulic cylinder under blocking; at two oil ports that connect actuator each first overload valve 11 in parallel or second overload valve 12; set its maximum overload power; if surpass this pressure; the first overload valve 11 and the second overload valve 12 are opened, and unload, and have protected hydraulic element and pipeline to avoid damaging.Power shovel is when excavating; swing arm is inevitable stressed; in order to safeguard normal operation; although the swing arm oil hydraulic cylinder is located and " off position ", must there be enough large blocking force to resist and stretches and compression, this locking pressure is sometimes well beyond the maximum service pressure of system; when this locking pressure during greater than the overload valve set pressure; overload valve is opened, and working oil pressure release oil return is protected other hydraulic element and pipeline.
The multi-way valve working principle: it is respectively system's main safety valve 3, leader unload valve 4 and load-sensitive reduction valve 5 that multi-way valve mainly contains the three functions control valve.System's relief valve 3 is controlled the Maximum operating pressure of multi-way valve system.Leader unload valve 4 is the leader unload valves 4 with pilot stage, and pilot stage is subjected to compensatory pressure and guide's spring contrast control, and main valve is subjected to load-reacting pump 1 pressure and spring action.During at meta, each sheet reverse valve oil head is obstructed when selector valve 7, and this moment, the load-sensitive compensatory pressure can be applied to the pilot stage of leader unload valve 4, leader unload valve 4 was opened, the 1 pressure off-load of load-reacting pump.When any selector valve 7 work, the load-sensitive compensatory pressure can pass through selector valve 7 oil return unloadings, the pilot valve of leader unload valve 4 can not opened, the control oil pressure that acts on leader unload valve 4 spring one ends can not pressure release, so leader unload valve 4 is in closed condition under the effect of load-reacting pump 1 pressure and spring.Each sheet of multi-way valve is when meta, load-reacting pump 1 output services flow is by leader unload valve 4 pressure release oil returns, load-reacting pump 1 output flow is very large, this moment, multi-way valve was at meta, each restriction is obstructed, and the load-sensitive compensatory pressure raises, and feeds back to the flow control valve 19 of load-reacting pump 1, the force value (oil return pressure reduction) that the load-sensitive compensatory pressure is set greater than load-reacting pump 1 is so load-reacting pump 1 flow reduces.during if any any a slice selector valve 7 work, load-sensitive compensatory pressure oil can be through pressure compensator 10 one-way valve pressure release oil returns, load-sensitive compensatory pressure oil pressure reduces, feed back to load-reacting pump 1 flow control valve 19, its load-reacting pump 1 output flow can be adjusted thereupon, in the time of selector valve 7 stroke maximum, load-sensitive compensatory pressure oil is hardly through the direct pressure release oil return of throttling, this moment, load-sensitive compensatory pressure pressure was roughly zero, load-reacting pump 1 output flow is maximum, load-reacting pump 1 is controlled under curve at power and is carried out Variable Control.The effect of load-sensitive compensatory pressure: as the stroking mechanism of feedback pressure signal feedback effect in load-reacting pump 1, make load-reacting pump 1 output flow adapt to all the time multi-way valve spool aperture needs, do not have unnecessary flow to run off, control to realize load-sensitive; Act on the oil circuit control of pressure compensator 10, control to realize pressure compensated flow.
The embodiment of multiple directional control valve system for return oil throttle control with load sensitive pressure compensation of the present invention, pressure compensator 10 flow controls: selector valve 7 oil circuits are provided with pressure compensator 10, when selector valve 7 monolithic work, pressure compensator 10 works independently, the load-sensitive compensatory pressure is adjusted load-reacting pump 1 output flow only as the induced pressure feedback signal.when multiple working (take any two actuators as example), if load F1 is greater than load F2, beginning induced pressure P1 is less than pressure P 2, a load-sensitive compensatory pressure part and spring are controlled each pressure compensator 10 1 ends together, another part acts on pressure compensator 10 the other ends or passes through valve rod meter out mouth pressure release oil return by the one-way valve of pressure compensator 10, so the load-sensitive compensatory pressure is taken from the minimum of each sheet selector valve 7 induced pressures, the inlet pressure compensation device 10 of starting working all is in normally open, become induced pressure Pm1 and induced pressure Pm2 after induced pressure P1 and induced pressure P2 are by pressure compensator 10, and Pm1 is less than Pm2, and act on pressure compensator 10 1 ends, the pressure compensator 10 of second selector valve can carry out throttling to induced pressure P2 under the effect of induced pressure Pm2, thereby induced pressure Pm2 is reduced until equate with induced pressure Pm1.
△P1=Pm1-PT
△P2=Pm2-PT=Pm1-PT=△P1
Q1=K×A1×△P1
m
Q2=K×A2×△P2
m
△ P1: the oil return pressure reduction of load F1; △ P2: the oil return pressure reduction of load F1; PT: return pressure
So Q1/Q2=A1/A2
Flow is according to spool oil return aperture size flow rate distribution, and irrelevant with load.
Claims (2)
1. multiple directional control valve system for return oil throttle control with load sensitive pressure compensation, it is by being provided with load-transducing mouth (2) and pumping the load-reacting pump (1) of hydraulic fluid port (18), flow control valve (19), pressure shut-off valve (20), power adjustments valve (21), the first variable oil cylinder (22), the second variable oil cylinder (24), swash plate (23), system's relief valve (3), leader unload valve (4), reduction valve (5), selector valve (7), the first one-way valve (8), execution work oil cylinder (9), the second one-way valve (14), pressure compensator (10), the first overload valve (11), the second overload valve (12), filter (15), throttle valve (16) and first is controlled mouthful (6), second controls mouthful (13) forms, and it is characterized in that pumping hydraulic fluid port (18) and system's relief valve (3), leader unload valve (4), the second one-way valve (14), filter (15) is communicated with, system's relief valve (3), leader unload valve (4), selector valve (7), the first overload valve (11), the second overload valve (12) is communicated with system oil return mouth (17), filter (15) is communicated with throttle valve (16), and throttle valve (16) is communicated with reduction valve (5), and reduction valve (5) is communicated with load-transducing mouth (2), the second one-way valve (14) is communicated with selector valve (7), selector valve (7), the first overload valve (11) and the second overload valve (12) are communicated with execution work oil cylinder (9) respectively, load-transducing mouth (2) is communicated with the first one-way valve (8), the first one-way valve (8) is communicated with pressure compensator (10), and pressure compensator (10) is communicated with selector valve (7), the outlet of load-reacting pump (1) is communicated with flow control valve (19), pressure shut-off valve (20), power adjustments valve (21), the first variable oil cylinder (22) respectively, flow control valve (19) is communicated with the second variable oil cylinder (24), flow control valve (19) is communicated with load-transducing mouth (2), the first variable oil cylinder (22) be connected the rod chamber of variable oil cylinder (24) and be connected with the swash plate (23) of load-reacting pump (1) respectively.
2. multiple directional control valve system for return oil throttle control with load sensitive pressure compensation according to claim 1, it is characterized in that the first variable oil cylinder (22) and the second variable oil cylinder (24) adjust the flow of load-reacting pump (1) by changing swash plate (23) pivot angle, the oil pressure that acts on the second variable oil cylinder (24) is higher, swash plate (23) pivot angle is less, and the flow output of load-reacting pump (1) is also just fewer; Power adjustments valve (21) is in right position under spring-force driven dual, the second variable oil cylinder (24) pressure oil is by power adjustments valve (21) oil return, and under oil pressure and spring action, swash plate (23) swings to large direction of the traffic in the first variable oil cylinder (22) chamber; In the first variable oil cylinder (22) chamber, oil pressure acts on push rod, push rod promotes lever makes lever around a spot wobble, promoting power adjustments valve (21) moves right, make power adjustments valve (21) be in left position, the pressure oil of load-reacting pump (1) enters the second variable oil cylinder (24) by power adjustments valve (21) through pressure shut-off valve (20), promote its piston rod, overcome the first variable oil cylinder (22) hydraulic coupling and Compress Spring swash plate (23) is swung to the small flow direction; Simultaneously because the first variable oil cylinder (22) piston rod moves to right, the arm of force that push rod promotes lever reduces, and the power that makes lever push away power adjustments valve (21) descends, until equate with power adjustments valve (21) spring force, swash plate (23) pivot angle is in new equilibrium position, thereby realizes power control.
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| CN 201010180155 CN101858368B (en) | 2010-05-13 | 2010-05-13 | Multiple directional control valve system for return oil throttle control with load sensitive pressure compensation |
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| CN 201010180155 CN101858368B (en) | 2010-05-13 | 2010-05-13 | Multiple directional control valve system for return oil throttle control with load sensitive pressure compensation |
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| CN101858368B true CN101858368B (en) | 2013-06-05 |
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| CN101324285A (en) * | 2008-07-30 | 2008-12-17 | 韩亚杰 | Limit flow hydraulic valve |
| CN101373027A (en) * | 2008-08-08 | 2009-02-25 | 锦州市力特缸泵阀液压制造有限公司 | Multi-way change valve |
-
2010
- 2010-05-13 CN CN 201010180155 patent/CN101858368B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3839268A1 (en) * | 1988-11-21 | 1990-05-23 | Kugelfischer G Schaefer & Co | Hydraulic compensating valve |
| CN1360156A (en) * | 2001-12-30 | 2002-07-24 | 深圳商巨自动化有限公司 | Combination valve |
| CN101324285A (en) * | 2008-07-30 | 2008-12-17 | 韩亚杰 | Limit flow hydraulic valve |
| CN101373027A (en) * | 2008-08-08 | 2009-02-25 | 锦州市力特缸泵阀液压制造有限公司 | Multi-way change valve |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101858368A (en) | 2010-10-13 |
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