CN103047212B - Hydraulic control reversing valve - Google Patents
Hydraulic control reversing valve Download PDFInfo
- Publication number
- CN103047212B CN103047212B CN201310005551.2A CN201310005551A CN103047212B CN 103047212 B CN103047212 B CN 103047212B CN 201310005551 A CN201310005551 A CN 201310005551A CN 103047212 B CN103047212 B CN 103047212B
- Authority
- CN
- China
- Prior art keywords
- valve
- spool
- valve port
- port
- pilot
- 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.)
- Active
Links
Landscapes
- Fluid-Pressure Circuits (AREA)
- Multiple-Way Valves (AREA)
Abstract
The invention relates to a hydraulic control reversing valve. The hydraulic control reversing valve is utilized in a hydraulic system, particularly in a high-pressure and large-flow hydraulic system, an electro-hydraulic control hydraulic system, a proportional control and servo-controlled hydraulic system and the like. The hydraulic control reversing valve is a main-stage valve with a double-spool structure and is characterized in that two spools (1 and 2) are located in a valve body side by side; and each spool is provided with upper valve ports (3 and 8) and lower valve ports (4 and 9) which form a difference fixed pressure reducing valve structure together with springs (7 and 10) so as to realize a pressure compensation function and enable pilot ends C to D and pilot ends E to F to maintain a constant low pressure. With the above structure, the valve has a two-way compensation function. The spools are capable of automatically following the opening size of two pilot valves (13 and 14) to move with no drive oil passage needed, and accordingly, directional control and flow control are realized. When the hydraulic control directional valve is utilized together with the pilot valves having various functions, rich application function can be achieved.
Description
Technical field
The present invention relates to a kind of pilot operated directional control valve, it is applied to hydraulic system, especially high-pressure high flux hydraulic power system, electrichydraulic control hydraulic system, proportional control and servocontrol hydraulic system etc.
Background technique
The electro-hydraulic reversing valve, hydraulicchange-over valve, proportional reversing valve, servovalve etc. that extensively adopt in high-pressure high-flow system, in ratio control system, in servo-control system are at present all the action realization commutation of two ends driving main valve plug and other relevant controls of by pilot valve, the pressure oil of guide's oil circuit being acted on main valve plug.This structure does not possess pressure compensation, and systematic function is restricted, and guide oil line structure is complicated, even needs an independent oil pump to provide low pressure oil for guide's oil circuit.Such as, proportional reversing valve is that pilot stage applies pressure oil to main valve plug two ends and spring force balance regulates valve port opening (valve port open area size) with proportional pressure-reducing valve, under the prerequisite not having pressure compensation, its flow is very large by load effect, is difficult to the proportional control of accomplishing flow.Pressure oil is acted on main valve plug two ends using nozzle-flapper structure or jet pipe structure as pilot stage and controls its aperture by servovalve.The multi-way reversing system adopted in engineering machinery, controls main valve by Manual pilot level by guide's oil circuit, is not having under pressure compensated prerequisite, and the speed of each cylinder is wayward by load effect, cannot realize multi-cylinder linkage.Pressure compensation is realized with series flow control valve in prior art, it is in series by a Fixed differential reducing valve and a throttle valve, it can form pressure compensation hydraulic system to realize commutation and speed regulating control together with selector valve, but it and selector valve are two discrete hydraulic element, this discrete structure brings very large trouble to the control of system, a lot of function cannot realize, function singleness.
Summary of the invention
For above-mentioned situation, the object of the present invention is just to provide a kind of pilot operated directional control valve: it possesses bidirection press compensate function, and it is controlled by pilot valve as the main valve of hydraulic system and provides permanent low-pressure pilot interface (guide's end) for pilot valve.
Solution of the present invention is: first spool and second spool are contained in two spool bore in valve body respectively, first spool and spool bore form two valve ports: valve port and first lower valve port in first, valve port opening moves axially with first spool and increases simultaneously or reduce, second spool and spool bore form two valve ports: valve port and second lower valve port in second, valve port opening moves axially with second spool and increases simultaneously or reduce, the axis of first spool, second spool is equipped with first spring, second spring respectively, and the direction acting on the spring force on spool is the direction that valve port is increased, two one-way valves are provided with: first one-way valve and second one-way valve at filler opening place, interior oil channel structures is: incoming pressure oil is divided into two, wherein a road connects the entrance point of valve port in first again after first one-way valve, the entrance point of valve port in second is connect again after another Lu Jingyi one-way valve, in first, the outlet end of valve port forms output terminal B after being communicated with the entrance point of second lower valve port, in second, the outlet end of valve port forms output terminals A after being communicated with the entrance point of first lower valve port, output terminals A and output terminal B draw two chambeies of the external oil hydraulic cylinder of valve or other hydraulic actuator, the outlet end of first lower valve port is drawn valve and is formed first return opening C outward, pressure oil is communicated with first spool epicoele by nail polish paths simultaneously, action of hydraulic force is in first epicoele face, first spool cavity of resorption is drawn valve and is formed first repairing mouth D outward, second lower valve port outlet end is drawn valve and is formed second return opening E outward, pressure oil is communicated with second spool epicoele by second asphalt channel simultaneously, action of hydraulic force is in second epicoele face, second spool cavity of resorption is drawn valve and is formed second repairing mouth F outward, first epicoele face, the hydraulic coupling that second epicoele face is born makes valve port reduce, first cavity of resorption face, the hydraulic coupling that second cavity of resorption face is born makes valve port increase, first return opening C-first repairing mouth D, second return opening E-second repairing mouth F forms two guide's ends: C-D end and E-F end, external pilot valve therebetween.
The above constitutes two Fixed differential reducing valve structures, plays pressure compensation effect, and under compensating coefficient, guide holds C-D and guide to hold the pressure of E-F to maintain a constant low pressure, and this pressure is referred to as: pilot pressure.Guide holds external pilot valve, controls keying and the aperture of pilot valve valve port, can realize commutation and flow control.
Accompanying drawing explanation
Fig. 1 is a kind of example structure of the present invention and hydraulic schematic thereof.
Fig. 2 is filler opening compound one-way valve structures schematic diagram of the present invention.
Fig. 3 is a kind of filler opening compound of the present invention one-way valve embodiment plan view.
Fig. 4 is A-A view of Fig. 3 of the present invention.
Fig. 5 is rating curve schematic diagram of the present invention.
Fig. 6 is another kind of embodiment's plan view of the present invention.
Fig. 7 is the left view of Fig. 6 of the present invention.
Fig. 8 is a kind of secondary pilot valve structural representation of the present invention.
Fig. 9 is a kind of hydraulic scheme of the present invention.
Embodiment
Below in conjunction with drawings and Examples, the present invention is described in further detail:
Provided by Fig. 1-Fig. 9, structure of the present invention is: first spool 1 and second spool 2 are contained in two spool bore in valve body 17 respectively, first spool 1 and spool bore form two valve ports: valve port 3 and first lower valve port 4 in first, valve port opening moves axially with first spool 1 and increases simultaneously or reduce, second spool 2 and spool bore form two valve ports: valve port 8 and second lower valve port 9 in second, valve port opening moves axially with second spool 2 and increases simultaneously or reduce, first spool 1, the axis of second spool 2 is equipped with first spring 7 respectively, second spring 10, the direction acting on the spring force on spool is the direction that valve port is increased, two one-way valves are provided with: first one-way valve 15 and second one-way valve 16 at filler opening place, interior oil channel structures is: incoming pressure oil is divided into two, wherein a road connects the entrance point of valve port 3 in first again after first one-way valve 15, the entrance point of valve port 8 in second is connect again after another Lu Jingyi one-way valve 16, in first, the outlet end of valve port 3 forms output terminal B after being communicated with the entrance point of second lower valve port 9, in second, the outlet end of valve port 8 forms output terminals A after being communicated with the entrance point of first lower valve port 4, output terminals A and output terminal B draw two chambeies of the external oil hydraulic cylinder of valve or other hydraulic actuator, the outlet end of first lower valve port 4 is drawn valve and is formed first return opening C outward, pressure oil is communicated with first spool epicoele by nail polish paths 18 simultaneously, action of hydraulic force is in first epicoele face 5, first spool cavity of resorption is drawn valve and is formed first repairing mouth D outward, the outlet end of second lower valve port 9 is drawn valve and is formed second return opening E outward, pressure oil is communicated with second spool epicoele by second asphalt channel 19 simultaneously, action of hydraulic force is in second epicoele face 11, second spool cavity of resorption is drawn valve and is formed second repairing mouth F outward, first epicoele face 5, the hydraulic coupling that second epicoele face 11 is born makes valve port reduce, first cavity of resorption face 6, the hydraulic coupling that second cavity of resorption face 12 is born makes valve port increase, first return opening C-first repairing mouth D, second return opening E-second repairing mouth F forms two guide's ends: C-D end and E-F end, external first pilot valve 13 therebetween, second pilot valve 14.
Described valve body 17 is one or split, and first spool 1, second spool 2 be distributed in a valve body or be distributed in two valve bodies respectively; Described first one-way valve 15, second one-way valve 16 be placed in first spool 1, second spool 2 place valve body 17 or be placed in this valve body 17 with exterior part; In the valve body 17 that described interior oil circuit is placed in first spool 1, second spool 2 place or a part be placed in parts beyond this valve body 17; Described first one-way valve 15, second one-way valve 16 or two compound one-way valves, the structure of compound one-way valve is, the one-way valve 22,24 being less than the little latus rectum of pilot pressure by a cracking pressure main one-way valve 26,27 parallel connection that again with one cracking pressure is greater than pilot pressure of connecting after a throttling pore 23,25 is formed; Described compound one-way valve or be together arranged in main inner elements of check valve 36 by the one-way valve 34 of little latus rectum and the throttling pore 35 that is cascaded is formed; In described first, in valve port 3, first lower valve port 4, second, valve port 8, second lower valve port 9 are cone valve structure or sliding valve structure; Valve port 8 in valve port 3, first lower valve port 4, second in described first, second lower valve port 9 be circumferentially continuous distributed, or circumferentially Disjunct distribution; Described nail polish paths 18, second asphalt channel 19 are the oil circuits of the little latus rectum being arranged on spool heart portion or are arranged on the oil circuit of the little latus rectum on valve body; Described first spool 1, second spool 2 are multidiameter shaft structure or overall isometrical axle construction; Described first spring 7, second spring 10 are Compress Spring or extension spring, when being Compress Spring, are arranged on the cavity of resorption of first spool 1 and the cavity of resorption of second spool 2, when being extension spring, are arranged on the epicoele of first spool 1 and the epicoele of second spool 2; Arrange small-sized third one-way valve 30 between described first spool 1, the upper and lower chamber of second spool 2 respectively, fourth one-way valve 31 plays pressure limiting effect, restriction upper cavity pressure is no more than a certain specified value.
From the above, Fig. 1 is the structural representation of an embodiment of the present invention and hydraulic system thereof: be exactly pilot operated directional control valve involved in the present invention within dotted line square frame, and part is external system in addition.The structure of this pilot operated directional control valve is: the first spool 1 that two structures are substantially identical and second spool 2 are contained in two spool bore in valve body 17, the structure that in spool bore inwall and spool outer round surface are provided with groove etc. and form, oil circuit is relevant with valve port, spool and spool bore are slidably matched, and spool can spool bore move axially relatively.First spool 1 and spool bore form two valve ports that reduce pressure: valve port 3 and first lower valve port 4 in first, and their valve port opening moves axially with first spool 1 and increases simultaneously or reduce.Form first epicoele face 5 and first cavity of resorption face 6 in the both ends of the surface of first spool 1 and shaft shoulder place, surround first spool 1 cavity of resorption with spool bore outside first cavity of resorption face 6, the outside in first epicoele face 5 and spool bore surround first spool 1 epicoele.Second spool 2 and spool bore also form two valve ports that reduce pressure: valve port 8 and second lower valve port 9 in second, and their valve port opening moves axially with second spool 2 and increases simultaneously or reduce.Form second epicoele face 11 and second cavity of resorption face 12 in the both ends of the surface of second spool 2 and shaft shoulder place, surround second spool 2 cavity of resorption with spool bore outside second cavity of resorption face 12, the outside in second epicoele face 11 and spool bore surround second spool 2 epicoele.The hydraulic coupling that first epicoele face 5, second epicoele face 11 are born makes valve port reduce, the hydraulic coupling that first cavity of resorption face 6, second cavity of resorption face 12 are born makes valve port increase, first spool 1, second spool 2 are separately installed with first spring 7, second spring 10, the spring force acted on spool makes valve port increase.
This pilot operated directional control valve also comprises the one-way valve that two are arranged on filler opening place: first one-way valve 15, second one-way valve 16.
The interior oil channel structures of this pilot operated directional control valve is: incoming pressure oil is divided into two, wherein a road connects the entrance point of valve port 3 in first again after first one-way valve 15, the entrance point of valve port 8 in second is connect again after another Lu Jingyi one-way valve 16, in first, the outlet end of valve port 3 forms output terminal B after being communicated with the entrance point of second lower valve port 9, in second, the outlet end of valve port 8 forms output terminals A after being communicated with the entrance point of first lower valve port 4, output terminals A and output terminal B draw two chambeies of the external oil hydraulic cylinder of valve or other hydraulic actuator, the outlet end of first lower valve port 4 is drawn valve and is formed first return opening C outward, its pressure oil is communicated with first spool 1 epicoele by the nail polish paths 18 of the little latus rectum in first spool heart portion, its action of hydraulic force is on first epicoele face 5, first spool 1 cavity of resorption is drawn valve and is formed first repairing mouth D outward, the outlet end of second lower valve port 9 is drawn valve and is formed second return opening E outward, its pressure oil is communicated with second spool 2 epicoele by the second asphalt channel 19 of the little latus rectum in second spool heart portion, its action of hydraulic force is on second epicoele face 11, second spool 2 cavity of resorption is drawn valve and is formed second repairing mouth F outward.C-D, E-F form two guide's ends, connect first pilot valve 13, second pilot valve 14 therebetween.
The above constitutes two Fixed differential reducing valve structures, plays pressure compensation effect.Under compensating coefficient, C-D end, E-F end pressure maintain a constant low pressure, i.e. pilot pressure (0.4MPa), in first on first spool 1, the keying of valve port 3 and first lower valve port 4 is just controlled by C-D end first pilot valve 13, and flow is only proportional with the valve port opening of first pilot valve 13, have nothing to do with load and charge oil pressure.In second on second spool 2, the keying of valve port 8 and second lower valve port 9 is controlled by E-F end second pilot valve 14, and flow is only proportional with the valve port opening of second pilot valve 14, has nothing to do with load and charge oil pressure.The valve port of such control first pilot valve 13, second pilot valve 14 opens and closes and aperture just can realize commutation and flow control.
In order to structure or (with) technologic convenience, described valve body 17 also can be split, and first spool 1 and second spool 2 can be contained in two valve bodies respectively; Described first one-way valve 15, second one-way valve 16 can be placed in the parts beyond valve body 17; A part of structure of described interior oil circuit can be arranged in the parts beyond valve body 17; Described nail polish paths 18, second asphalt channel 19 also can be the little latus rectum oil circuits be arranged on valve body.
Four kinds of working staties of this valve:
State one, C-D holds closedown, and E-F end is opened (namely C-D holds first pilot valve 13 to close, and E-F holds second pilot valve 14 to open):
When C-D end is closed, C mouth pressure raises and acts on first epicoele face 5, and first spool 1 is moved to left, and close valve port 3 and first lower valve port 4 in first, oil inlet P 1 and return opening C are blocked simultaneously simultaneously.At this moment E-F end is opened, and the E mouth pressure acting on second epicoele face 11 reduces, and second spring 10 promotes second spool 2 and moves to left, and valve port 8 and lower valve port 9 are opened simultaneously.Pressure oil moves to right from P2 → A mouth → oil hydraulic cylinder left chamber → promotion piston, oil hydraulic cylinder right cavity pressure oil → B mouth → E mouth → second pilot valve 14 → oil sump.There is a kind of reverse feedback relation and make E-F end group this is constant voltage in valve port 8 in E mouth pressure and second, second lower valve port 9 under compensating coefficient: if certain reason makes E mouth pressure raise, then pressure acts in second that on cavity area 11, it makes the aperture of valve port 8 in second, second lower valve port 9 reduce by overcoming spring force, valve port pressuring drop increases, E mouth pressure falls after rise thereupon, and vice versa.So can the valve port opening of second pilot valve 14 be held to control flow by control E-F and have nothing to do with load and charge oil pressure.
That is: C-D end is closed, and E-F holds unlatching, and hydraulic oil flows out from A mouth, and B mouth flows into, and holds the valve port opening of second pilot valve 14 to control flow by control E-F.
State two, E-F holds closedown, and C-D holds unlatching:
In like manner, when E-F end is closed, when C-D end is opened, pressure oil flows out from B mouth, and A mouth flows into.Hold the valve port opening of first pilot valve 13 to control flow by control C-D, have nothing to do with load and charge oil pressure.
State three, C-D holds and E-F end is all closed:
When C-D end and E-F hold all close time, in first, in valve port 3 and first lower valve port 4, second, valve port 8 and second lower valve port 9 are all closed.A mouth and B mouth, P1 mouth and P2 mouth are cut off, and piston is in blocking.
State four, C-D holds and E-F holds full open:
When C-D end and E-F end are all opened enough large, pressure oil is from valve port 3 → second lower valve port 9 → E mouth → second pilot valve 14 → oil sump off-load P1 mouth → first.Pressure oil is also from valve port 8 → first lower valve port 4 → C mouth → first pilot valve 13 → oil sump off-load P2 → second.At this moment piston is in free state.
In order to the normal work of valve, be provided with first one-way valve 15, second one-way valve 16 at filler opening place.When this valve is operated in state four, pressure oil is in unloading condition, after state one (C-D end is closed E-F end and opened) conversion, the pressure that the first epicoele face 5 of first spool 1 is born does not reach pilot pressure and can not be closed, and pressure oil valve port 3, second lower valve port 9, E mouth, first pilot valve 14 in P1, first continue off-load to oil sump.To change must first be transitioned into after state three makes first spool 1 close to state one and be transformed into state one again.In order to overcome this shortcoming, described first one-way valve 15, second one-way valve 16 can adopt two compound one-way valves to replace, and Fig. 2 is its structural representation: they are all that main one-way valve 26,27 parallel connection being greater than pilot pressure by again with one cracking pressure after a cracking pressure is connected lower than one-way valve 22,24 and throttling pore 23,25 of the little latus rectum of pilot pressure is formed.Close due to C-D end like this and pass through without flow, the first epicoele face 5 being transferred the pressure to first spool 1 higher than the P mouth pressure of pilot pressure by valve port 8 in the one-way valve 24 of throttling pore 25, little latus rectum, P2, second, first lower valve port 4 make first spool 1 close, make this valve directly be transformed into state one from state four, change in like manner to state two.Fig. 3 is a kind of filler opening compound of the present invention one-way valve embodiment plan view, and Fig. 4 is the A-A view of Fig. 3, and in described compound one-way valve, the one-way valve 34 of little latus rectum, throttling pore 35 are arranged in series in main inner elements of check valve 36.
Compensating basin and non-compensating basin:
In state one and state two times, this kind of pilot operated directional control valve can be operated in compensating basin and non-compensating basin.Suppose that C-D end is closed E-F end and opened, then by the flow of its second pilot valve 14 be:
Q---E mouth flow
Ca---valve port flow coefficient
The valve port opening (valve port open area) of A---second pilot valve 14.
Δ p
e-F---E-F end pressure is poor.
ρ---fluid density.
Because E-F end pressure difference Δ p is constant voltage, so flow q is only directly proportional to the valve port area A of second pilot valve 14, scaling factor is
if the supply flow of pump is q in Fig. 1
0, oil hydraulic cylinder rodless cavity piston area is S
a, rod chamber piston area is S
b.As shown in Figure 5: in compensating basin, when the valve port area A of second pilot valve 14 increases gradually from zero, the proportional increase of E mouth flow q, when A increases to A
0shi Liuliang reaches
later flow q no longer increases with valve port area A and increases, and valve enters non-compensating basin.The boundary line of compensating basin and non-compensating basin is decided by the supply flow q of pump
0.When compensating basin, in Fig. 1, in second, valve port 8, second lower valve port 9 are in decompression state, simultaneously relief valve overflow.When being operated in non-compensating basin, in second, valve port 8, second lower valve port 9 are all opened, and P mouth flow equals the supply flow of pump, and relief valve is overflow no longer.The a little higher than induced pressure of delivery side of pump pressure.
In FIG, in described first, in valve port 3, first lower valve port 4, second, valve port 8, second lower valve port 9 have employed cone valve structure, and valve port is continuous distributed circumferentially.Described first spool 1, second spool 2 have employed multidiameter shaft structure.Described first spring 7, second spring 10 are Compress Springs, should be arranged in the cavity of resorption of first spool 1 and the cavity of resorption of second spool 2 when being Compress Spring.
Fig. 6, Fig. 7 are an alternative embodiment of the invention, and in described first, in valve port 3, first lower valve port 4, second, valve port 8, second lower valve port 9 have employed sliding valve structure.Valve port 8, second lower valve port 9 circumferentially Disjunct distribution in this example in valve port 3, first lower valve port 4, second in described first, it is made up of the breach 33 of circumferentially Disjunct distribution some on spool.Described first spool 1 and second spool 2, have employed overall grade for gauge structure.Described first spring 7 and second spring 10 have employed extension spring, should be arranged on the epicoele of first spool 1 and the epicoele of second spool 2 when being extension spring.Described first spool 1 and second spool 2, heart position is provided with small-sized third one-way valve 30 respectively and is communicated with upper and lower chamber with fourth one-way valve 31 and plays pressure limiting effect wherein, when spool closedown causes upper cavity pressure too high because leaking, pressure oil opens the third one-way valve 30 or fourth one-way valve 31, within upper cavity pressure is limited in a certain required value (1MPa).The force value of this Embodiment C-D end and E-F end is:
Spool is opened and is operated in compensating basin (pilot pressure) 0.4MPa
Spool unlatching is operated in non-compensating basin and is less than 0.4MPa
Spool is closed and is less than 1MPa
The structure of pilot valve:
Pilot operated directional control valve involved in the present invention is a kind of main valve, and its pilot valve structure is not content involved in the present invention.Pilot valve is arranged on C-D end and E-F end, is a kind of simple low pressure two-way structure.The pilot valve of this kind of pilot operated directional control valve and various difference in functionality is supporting obtains abundant application function.Pilot valve can be direct dynamic structure, also can adopt the secondary guide structure shown in Fig. 8.After the coupling of one-level pilot valve 38, what export to secondary pilot valve 39 is a low-pressure low flow oil circuit, and it is equivalent to a signal oil circuit, makes secondary pilot valve 39 can adopt miniature small-power valve.
For the ease of better understanding the function of this valve, below provide an application example of the present invention:
Fig. 9 is a multi-cylinder parallel system be made up of this pilot operated directional control valve.Connecting two proportional throttle valves 43 respectively at two guide's ends of this pilot operated directional control valve can composition flow control circuit.Fuel feeding part adopts constant-pressure variable pump 44 fuel feeding, and relief valve 45 plays safety valve effect.General multi-cylinder parallel system due to the speed of each cylinder wayward by the impact of load and charge oil pressure, and each cylinder speed of multi-cylinder parallel system of this pilot operated directional control valve composition is not subject to the impact of load and charge oil pressure, independently be controlled by control signal, realize multi-cylinder linkage.This parallel system can be applicable to engineering loading, excavation machinery, realizes the controlled interlock of multi-cylinder, and performance is better than the multi-way reversing system used at present.
Compared to the prior art the present invention has following outstanding feature:
1, this pilot operated directional control valve possesses bidirection press compensate function, automatically can adapt to load variations, adapt to charge oil pressure change, make two guides hold maintenance constant low pressure.Not only capable of reversing but also be convenient to flow control.Effectively reduce the frictional force of pilot valve core, hydraulic power and leakage simultaneously, be conducive to action message and the effective sealing of pilot valve, simplify pilot valve structure.
2, this pilot operated directional control valve need not additional driving oil circuit, without the need to separately establishing pressure compensation oil circuit, it constitute the high pressure main passage of hydraulic system, and pilot valve is only a low pressure two-way simple structure.This feature makes system summary structure simplify, and is convenient to the large-scale integrated of complicated oil circuit.
3, this pilot operated directional control valve adapts to high-pressure high-flow system, and its performance is better than electro-hydraulic reversing valve, the high-pressure high-flow system of two-way plug-in valve composition.
4, this pilot operated directional control valve adapts to electrichydraulic control, proportional control and servocontrol, and can form multi-cylinder linkage system, performance is better than proportional direction valve.
Claims (10)
1. a pilot operated directional control valve, comprises valve body, spool, spool bore and interior oil circuit, it is characterized in that:
A) first spool (1) and second spool (2) are contained in two spool bore in valve body (17) respectively, first spool (1) and spool bore form two valve ports: valve port (3) and first lower valve port (4) in first, valve port opening moves axially with first spool (1) and increases simultaneously or reduce, second spool (2) and spool bore form two valve ports: valve port (8) and second lower valve port (9) in second, valve port opening moves axially with second spool (2) and increases simultaneously or reduce, first spool (1), the axis of second spool (2) is equipped with first spring (7) respectively, second spring (10), the direction acting on the spring force on spool is the direction that valve port is increased,
B) two one-way valves are provided with at filler opening place: first one-way valve (15) and second one-way valve (16);
C) in, oil channel structures is: incoming pressure oil is divided into two, wherein a road connects the entrance point of valve port in first (3) again after first one-way valve (15), the entrance point of valve port in second (8) is connect again after another Lu Jingyi one-way valve (16), in first, the outlet end of valve port (3) forms output terminal B after being communicated with the entrance point of second lower valve port (9), in second, the outlet end of valve port (8) forms output terminals A after being communicated with the entrance point of first lower valve port (4), output terminals A and output terminal B draw two chambeies of the external oil hydraulic cylinder of valve or other hydraulic actuator, the outlet end of first lower valve port (4) is drawn valve and is formed first return opening C outward, pressure oil is communicated with first spool epicoele by nail polish paths (18) simultaneously, action of hydraulic force is in first epicoele face (5), first spool cavity of resorption is drawn valve and is formed first repairing mouth D outward, second lower valve port (9) outlet end is drawn valve and is formed second return opening E outward, pressure oil is communicated with second spool epicoele by second asphalt channel (19) simultaneously, action of hydraulic force is in second epicoele face (11), second spool cavity of resorption is drawn valve and is formed second repairing mouth F outward, first epicoele face (5), second epicoele face (11) hydraulic coupling of bearing makes valve port reduce, first cavity of resorption face (6), second cavity of resorption face (12) hydraulic coupling of bearing makes valve port increase, first return opening C-first repairing mouth D, second return opening E-second repairing mouth F forms two guides and holds C-D, E-F, external first pilot valve (13) therebetween, second pilot valve (14).
2. pilot operated directional control valve as claimed in claim 1, is characterized in that: described valve body (17) is one or split, and first spool (1), second spool (2) are distributed in a valve body or are distributed in respectively in two valve bodies.
3. pilot operated directional control valve as claimed in claim 1, it is characterized in that: described first one-way valve (15), second one-way valve (16) be placed in first spool (1), second spool (2) place valve body (17) or be placed in this valve body (17) with exterior part, in the valve body (17) that interior oil circuit is placed in first spool (1), second spool (2) place or a part be placed in parts beyond this valve body (17).
4. pilot operated directional control valve as claimed in claim 1, it is characterized in that: described first one-way valve (15), second one-way valve (16) are two compound one-way valves, the structure of compound one-way valve is, the one-way valve (22,24) being less than the little latus rectum of pilot pressure by a cracking pressure main one-way valve (26, the 27) parallel connection that again with one cracking pressure is greater than pilot pressure of connecting after a throttling pore (23,25) is formed.
5. pilot operated directional control valve as claimed in claim 4, is characterized in that: described compound one-way valve is arranged on by the one-way valve of little latus rectum (34) and the throttling pore (35) that is cascaded that main inner elements of check valve (36) is interior to be formed.
6. pilot operated directional control valve as claimed in claim 1, it is characterized in that: in described first, in valve port (3), first lower valve port (4), second, valve port (8), second lower valve port (9) are cone valve structure or sliding valve structure, valve port (8), second lower valve port (9) circumferentially continuous distributed or circumferentially Disjunct distribution in valve port (3), first lower valve port (4), second in first.
7. pilot operated directional control valve as claimed in claim 1, is characterized in that: described nail polish paths (18), second asphalt channel (19) are the oil circuits of the little latus rectum being arranged on spool heart portion or are arranged on the oil circuit of the little latus rectum on valve body.
8. pilot operated directional control valve as claimed in claim 1, it is characterized in that: described first spring (7), second spring (10) are Compress Spring or extension spring, when being Compress Spring, be arranged on the cavity of resorption of first spool (1) and the cavity of resorption of second spool (2), when being extension spring, be arranged on the epicoele of first spool (1) and the epicoele of second spool (2).
9. pilot operated directional control valve as claimed in claim 1, is characterized in that: described first spool (1), second spool (2) are multidiameter shaft structure or overall isometrical axle construction.
10. pilot operated directional control valve as claimed in claim 1, is characterized in that: arrange small-sized third one-way valve (30) between described first spool (1), the upper and lower chamber of second spool (2) respectively, fourth one-way valve (31) plays pressure limiting effect.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310005551.2A CN103047212B (en) | 2013-01-08 | 2013-01-08 | Hydraulic control reversing valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310005551.2A CN103047212B (en) | 2013-01-08 | 2013-01-08 | Hydraulic control reversing valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103047212A CN103047212A (en) | 2013-04-17 |
| CN103047212B true CN103047212B (en) | 2015-04-01 |
Family
ID=48059992
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310005551.2A Active CN103047212B (en) | 2013-01-08 | 2013-01-08 | Hydraulic control reversing valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103047212B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106122142B (en) * | 2016-06-24 | 2018-08-17 | 平高集团有限公司 | Integrated form hydraulic control one-way valve |
| CN107795279B (en) * | 2017-12-06 | 2024-07-30 | 江苏徐工工程机械研究院有限公司 | Drilling machine and engineering vehicle |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2701509C2 (en) * | 1977-01-15 | 1985-10-31 | Robert Bosch Gmbh, 7000 Stuttgart | Hydraulic control device for at least two hydraulic consumers |
| JP3534324B2 (en) * | 1994-07-12 | 2004-06-07 | 株式会社小松製作所 | Pressure compensating valve |
| JPH11201107A (en) * | 1998-01-12 | 1999-07-27 | Hitachi Constr Mach Co Ltd | Pressure compensation valve |
| CN2448975Y (en) * | 2000-10-30 | 2001-09-19 | 孙茂钊 | Autoamtic reversal valve for electric controlled hydraulic actuator |
| DE10240602A1 (en) * | 2002-09-03 | 2004-03-18 | Daimlerchrysler Ag | Control valve for automatic transmission gear of vehicle, comprising compensating element attached to front of sliding device |
| CN201874913U (en) * | 2010-12-07 | 2011-06-22 | 上海诺玛液压系统有限公司 | Multi-way valve with pressure compensation mechanism |
| CN102734246B (en) * | 2012-07-13 | 2016-01-20 | 三一汽车制造有限公司 | Hydrovalve and pressure compensating method, hydraulic valve bank, hydraulic system and engineering machinery |
-
2013
- 2013-01-08 CN CN201310005551.2A patent/CN103047212B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN103047212A (en) | 2013-04-17 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN202673874U (en) | Constant-pressure variable control system of load sensitive hydraulic pump | |
| CN100414154C (en) | Direct action type proportional pressure-reducing valve | |
| CN105971964A (en) | Multiway electro-hydraulic control valve adopting oil return differential pressure as pilot oil source | |
| CN113464514B (en) | Integrated electric control multi-way valve and crane | |
| CN103343759A (en) | Dual-purpose multi-channel hydraulic proportional valve | |
| CN104032791A (en) | Quantitative and variable hydraulic system of loading machine | |
| US20200096022A1 (en) | Hydraulic fluid pressure compensator unit with integrated load sense and reverse flow checks | |
| US20200386246A1 (en) | Hydraulic valve with pressure limiter function | |
| EP3505775A1 (en) | Hydraulic no-back device | |
| CN104989690A (en) | Overload relief valve | |
| DE102012007108A1 (en) | Valvistor arrangement has pilot branch, in which pilot valve and associated pressure regulator are arranged, where pressure regulator is arranged downstream of pilot valve | |
| CN103047212B (en) | Hydraulic control reversing valve | |
| CN108223493A (en) | A kind of variable balanced valve of pilot ratio | |
| CN109306976B (en) | Load sensitive control system | |
| CN102678650B (en) | Double-pump converging oil-filling valve | |
| EP0862698B1 (en) | Control valves | |
| CN220487970U (en) | Hydraulic control floating load sensitive hydraulic system and electric arm vehicle | |
| US10612567B2 (en) | Valve device | |
| WO2006105765A1 (en) | Directional control valve and control system provided therewith | |
| CN105402449B (en) | Hydraulic control one-way valve | |
| CN113983017B (en) | Multi-way valve reversing linkage and hydraulic system | |
| CN200975530Y (en) | Direct-action proportional relief pressure valve | |
| CN204704187U (en) | Overload unloading valve | |
| CN114076127B (en) | Rotary balance valve and rotary hydraulic system | |
| CN210106282U (en) | Load feedback pressure compensation pilot valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |