CN203879835U - Balance valve, counterweight oil cylinder hydraulic control system and vertical support leg oil cylinder hydraulic control system - Google Patents
Balance valve, counterweight oil cylinder hydraulic control system and vertical support leg oil cylinder hydraulic control system Download PDFInfo
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- CN203879835U CN203879835U CN201420272138.2U CN201420272138U CN203879835U CN 203879835 U CN203879835 U CN 203879835U CN 201420272138 U CN201420272138 U CN 201420272138U CN 203879835 U CN203879835 U CN 203879835U
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- 238000013016 damping Methods 0.000 claims abstract description 138
- 239000003921 oil Substances 0.000 claims abstract description 110
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 38
- 239000000945 filler Substances 0.000 claims description 22
- 230000002457 bidirectional effect Effects 0.000 claims description 3
- 239000007788 liquid Substances 0.000 abstract 2
- 230000000694 effects Effects 0.000 description 11
- 238000011144 upstream manufacturing Methods 0.000 description 10
- 230000009471 action Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 3
- 230000005611 electricity Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
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Abstract
The utility model provides a balanced valve, counter weight hydro-cylinder liquid accuse system and perpendicular landing leg hydro-cylinder liquid accuse system. Wherein the balanced valve includes: a first check valve; the first end of the first damping hole is communicated with the oil inlet of the first one-way valve, and the second end of the first damping hole is communicated with the oil outlet of the first one-way valve; the first hydraulic control one-way valve is communicated with the first one-way valve and the first damping hole respectively; when the first check valve is in a conducting state, the oil pressure of a control oil port of the first hydraulic control check valve is zero, and hydraulic oil flows through the first check valve and the first hydraulic control check valve; under the non-conducting state of the first check valve, the control oil port of the first hydraulic control check valve is provided with oil pressure, and the hydraulic oil flows through the first damping hole and the first hydraulic control check valve. The technical scheme of the utility model can realize the throttle speed governing to hydraulic oil under the condition that does not increase cost, make the operation of working part stable, reduce the impact that causes the hydraulic control system.
Description
Technical field
The utility model relates to engineering machinery, in particular to a kind of equilibrium valve, counterweight oil cylinder hydraulic control system and vertical support oil cylinder hydraulic control system.
Background technique
The counterweight of getting on the bus of large-scale crawler crane generally all has self-loading and self-unloading functions, and this function realizes by two weight balancing oil cylinders.In order to ensure weight balancing oil cylinder decline stationarity and can stop at an arbitrary position, equilibrium valve all will be installed on weight balancing oil cylinder, can ensure the steady decline of weight balancing oil cylinder, can ensure again locked at an arbitrary position.
In conjunction with referring to Fig. 1, for existing a kind of counterweight oil cylinder hydraulic control system, the wherein oil inlet P of [constant 4 ' and selector valve 3 ' ' be connected, the first actuator port A ' of selector valve 3 ' is connected with equilibrium valve 2 ', equilibrium valve 2 ' is connected with the rodless cavity 12 ' of weight balancing oil cylinder 1 ', the second actuator port B ' of selector valve 3 ' is connected with the rod chamber 11 ' of weight balancing oil cylinder 1 ', and the hydraulic control hydraulic fluid port of equilibrium valve 2 ' is connected with the second actuator port B ' of selector valve 3 '.
Complete counterweight promotes and decline process is:
1, [constant 4 ' setting pressure, higher than the required pressure 4MPA of load left and right, guarantees to mention load;
2, selector valve 3 ' right side electromagnet obtains electric, right position enters working state, hydraulic oil is from the oil inlet P of selector valve 3 ' ' flow to the first actuator port A ', then enter the rodless cavity 12 ' of weight balancing oil cylinder 1 ' by the one-way valve of equilibrium valve 2 ', hydraulic oil in rod chamber 11 ' flows to oil return inlet T from the second actuator port B ' of selector valve 3 ' ', realize the lifter motion of counterweight;
3, the electromagnet dead electricity of selector valve 3 ', meta enters working state, weight balancing oil cylinder 1 ' stop motion, under equilibrium valve 2 ' closed condition in locking state;
4, the left side electromagnet of selector valve 3 ' obtains electric, left position enters working state, hydraulic oil is from the oil inlet P of selector valve 3 ' ' flow to the second actuator port B ', then enter the rod chamber 11 ' of weight balancing oil cylinder 1 ', the control port oil-feed of equilibrium valve 2 ' simultaneously, promotes main valve plug and opens, and the hydraulic oil in the rodless cavity 12 ' of weight balancing oil cylinder 1 ' flows into the first actuator port A ' of selector valve 3 ' by the main valve plug of equilibrium valve 2 ', finally pass through oil return inlet T ' flow out, realize the descending motion of counterweight.
The defect that prior art scheme exists is, for cost-saving, equilibrium valve 2 ' is actually an one way sequence valve, and valve core structure is simple, formerly lead pressure-acting lower valve core or in full-gear, in closed condition, can not realize valve core opening according to the proportional variation of pilot pressure, cause selector valve 3 ' in the time of the extremely left position of commutation, hydraulic fluid flow rate is excessive, the decline moment of weight balancing oil cylinder 1 ' produces larger shake, reduces each component working life-span, easily produces potential safety hazard.
Model utility content
The utility model aims to provide a kind of equilibrium valve, counterweight oil cylinder hydraulic control system and vertical support oil cylinder hydraulic control system, can be in the situation that not increasing cost, realize the throttle grverning to hydraulic oil, make the stable of workpiece, reduce the impact that hydraulic control system is caused.
To achieve these goals, according to an aspect of the present utility model, provide a kind of equilibrium valve, having comprised: the first one-way valve; The first damping hole, the first end of the first damping hole is communicated with the filler opening of the first one-way valve, and the second end of the first damping hole is communicated with the oil outlet of the first one-way valve; And first Pilot operated check valve, the first Pilot operated check valve is communicated with the first one-way valve and the first damping hole respectively; Under the state of the first one-way valve conducting, the control port oil pressure of the first Pilot operated check valve is zero, hydraulic oil flow through the first one-way valve and the first Pilot operated check valve; Under the state of the first not conducting of one-way valve, the control port of the first Pilot operated check valve has oil pressure, hydraulic oil flow through the first damping hole and the first Pilot operated check valve.
Further, equilibrium valve also comprises the second damping hole to be opened/closed, and the first end of the second damping hole is communicated with the filler opening of the first one-way valve, and the second end of the second damping hole is communicated with the oil outlet of the first one-way valve.
Further, the first Pilot operated check valve is communicated with the filler opening of the first one-way valve and the first end of the first damping hole respectively.
Further, equilibrium valve also comprises: the second one-way valve; And second Pilot operated check valve, the second Pilot operated check valve is communicated with the second one-way valve, and the second Pilot operated check valve and the first Pilot operated check valve form bidirectional hydraulic lock.
Further, equilibrium valve also comprises the 3rd damping hole, and the first end of the 3rd damping hole is communicated with the filler opening of the second one-way valve, and the second end of the 3rd damping hole is communicated with the oil outlet of the second one-way valve.
Further, the second Pilot operated check valve is communicated with the filler opening of the second one-way valve and the first end of the 3rd damping hole respectively.
Further, equilibrium valve also comprises the 4th damping hole to be opened/closed, and the first end of the 4th damping hole is communicated with the filler opening of the second one-way valve, and the second end of the 4th damping hole is communicated with the oil outlet of the second one-way valve.
According on the other hand of the present utility model, a kind of counterweight oil cylinder hydraulic control system is provided, comprising: weight balancing oil cylinder; Equilibrium valve, equilibrium valve is communicated with the rodless cavity of weight balancing oil cylinder; And selector valve, the first actuator port of selector valve is communicated with equilibrium valve, and the second actuator port of selector valve is communicated with the rod chamber of weight balancing oil cylinder; Equilibrium valve is aforesaid equilibrium valve, and the control port of the first Pilot operated check valve is communicated with the second actuator port of selector valve.
According on the other hand of the present utility model, a kind of counterweight oil cylinder hydraulic control system is provided, comprising: weight balancing oil cylinder; Equilibrium valve, equilibrium valve is communicated with the rodless cavity of weight balancing oil cylinder; And selector valve, the first actuator port of selector valve is communicated with equilibrium valve, and the second actuator port of selector valve is communicated with the rod chamber of weight balancing oil cylinder; Equilibrium valve is aforesaid equilibrium valve, and the first actuator port of selector valve is communicated with the first Pilot operated check valve, and the oil outlet of the first one-way valve is communicated with the rodless cavity of weight balancing oil cylinder, and the control port of the first Pilot operated check valve is communicated with the second actuator port of selector valve.
According on the other hand of the present utility model, a kind of vertical support oil cylinder hydraulic control system is provided, comprise equilibrium valve, equilibrium valve is aforesaid equilibrium valve.
Application the technical solution of the utility model, equilibrium valve comprises the first one-way valve, the first damping hole and the first Pilot operated check valve, wherein the filler opening of the first one-way valve is communicated with the first end of the first damping hole, the oil outlet of the first one-way valve is communicated with the second end of the first damping hole, the first Pilot operated check valve is communicated with the first one-way valve and the first damping hole respectively, the first one-way valve in parallel with the first damping hole after, oil circuit in parallel is connected with the first Pilot operated check valve.Under the state of the first one-way valve conducting, the control port oil pressure of the first Pilot operated check valve is zero, because the resistance of the first damping hole is excessive, hydraulic oil flows into actuator through the first one-way valve and the first Pilot operated check valve, can realize actuator and move comparatively fast; Under the state of the first not conducting of one-way valve, the control port of the first Pilot operated check valve has oil pressure, hydraulic oil need to could be realized proper flow through the first damping hole and the first Pilot operated check valve, and the first damping hole has ensured in running of hydraulic power oil process all the time in throttle grverning state, the motion of actuator is comparatively steady, there will not be larger vibration, has reduced the impact to hydraulic control system, extend the working life of each parts, improved the Security of hydraulic control system.
Brief description of the drawings
The Figure of description that forms the application's a part is used to provide further understanding of the present utility model, and schematic description and description of the present utility model is used for explaining the utility model, does not form improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 shows according to the schematic diagram of the counterweight oil cylinder hydraulic control system of prior art;
Fig. 2 shows according to the schematic diagram of first embodiment's of the present utility model equilibrium valve;
Fig. 3 shows according to the schematic diagram of second embodiment's of the present utility model equilibrium valve; And
Fig. 4 shows according to first embodiment's of the present utility model equilibrium valve and is applied to the schematic diagram in counterweight oil cylinder hydraulic control system.
Description of reference numerals:
1 ', weight balancing oil cylinder; 11 ', rod chamber; 12 ', rodless cavity; 2 ', equilibrium valve; 3 ', selector valve; 4 ', [constant; 1, weight balancing oil cylinder; 11, rod chamber; 12, rodless cavity; 2, equilibrium valve; 21, the first one-way valve; 22, the first Pilot operated check valve; 23, the first damping hole; 24, the second damping hole; 25, the second Pilot operated check valve; 26, the second one-way valve; 27, the 3rd damping hole; 28, the 4th damping hole; 3, selector valve; 4, [constant.
Embodiment
Describe below with reference to the accompanying drawings and in conjunction with the embodiments the utility model in detail.It should be noted that, in the situation that not conflicting, the feature in embodiment and embodiment in the application can combine mutually.
As shown in Figure 2, according to first embodiment of the present utility model, a kind of equilibrium valve 2 is provided, comprise the first one-way valve 21, the first damping hole 23 and the first Pilot operated check valve 22, wherein the first end of the first damping hole 23 is communicated with the filler opening of the first one-way valve 21, the second end of the first damping hole 23 is communicated with the oil outlet of the first one-way valve 21, the first Pilot operated check valve 22 is communicated with the first one-way valve 21 and the first damping hole 23 respectively, the first damping hole 23 in parallel with the first one-way valve 21 after, parallel pipeline is connected with the first Pilot operated check valve 22.Equilibrium valve 2 has two kinds of working staties, the first is that hydraulic oil flows to C1 mouth from the V1 mouth of equilibrium valve 2, these direction first one-way valve 21 conductings, the control port C2 oil pressure of the first Pilot operated check valve 22 is zero simultaneously, the control port C2 of the first Pilot operated check valve 22 does not open, the first Pilot operated check valve 22 can only be along forward conduction, oppositely can not conducting, hydraulic oil flows out from equilibrium valve 2 through the first Pilot operated check valve 22 and the first one-way valve 21, because first damping hole 23 resistances in parallel with the first one-way valve 21 are excessive, hydraulic oil can be through the first damping hole 23, first one-way valve 21 of almost all flowing through flows to the C1 mouth of equilibrium valve 2, hydraulic oil flows into actuator from the C1 mouth of equilibrium valve 2 flows out, can the quick acting of pushing executing mechanism forward, the second state is that hydraulic oil flows to V1 mouth from the C1 mouth of equilibrium valve 2, these direction first one-way valve 21 not conductings, the control port C2 of the first Pilot operated check valve 22 has oil pressure simultaneously, i.e. the first Pilot operated check valve 22 reverse-conductings, hydraulic oil can only flow to the first damping hole 23, flow out the V1 mouth of equilibrium valve 2 through the first damping hole 23 and the first Pilot operated check valve 22, drive actuator's counteragent, and due to the throttle grverning effect of the first damping hole 23, the counteragent that makes actuator carries out with velocity-stabilization comparatively slowly all the time, avoid the impact to equilibrium valve 2 and whole hydraulic control system, extend the working life of each parts, improve the Security of hydraulic control system.
Preferably, equilibrium valve 2 is board mounting structure, can be directly installed in actuator, is simple and easy to dismounting.
Preferably, equilibrium valve 2 also comprises the second damping hole 24, the first end of the second damping hole 24 is communicated with the filler opening of the first one-way valve 21, the second end of the second damping hole 24 is communicated with the oil outlet of the first one-way valve 21, the first damping hole 23, the second damping hole 24 and the first one-way valve 21 are parallel with one another, and the first Pilot operated check valve 22 is communicated with parallel pipeline.The second damping hole 24 is adjustable damping hole, can select according to actual needs to open or close, and also can select as required the aperture of opening simultaneously.The second damping hole 24 can be, just to open in the time that the first damping hole 23 stops up in normally off as the spare unit of the first damping hole 23, guarantees the Flow-rate adjustment effect of hydraulic control system; Also can be the accessory as the first damping hole 23, can not meet while adjusting stream needs and the first damping hole 23 is opened at the first damping hole 23 simultaneously, meet better the Flow-rate adjustment requirement of system.
Preferably, the first Pilot operated check valve 22 is positioned at the upstream of the first one-way valve 21, and the first Pilot operated check valve 22 is communicated with filler opening, the first end of the first damping hole 23 and the first end of the second damping hole 24 of the first one-way valve 21 respectively.With the downstream comparison that the first Pilot operated check valve 22 is arranged in to the first one-way valve 21; when the upstream that the first Pilot operated check valve 22 is arranged in to the first one-way valve 21 can ensure actuator's counteragent; can there is not dither in the first Pilot operated check valve 22, effectively protect the first Pilot operated check valve 22.
Certainly, this does not also mean that the first Pilot operated check valve 22 can only be arranged in the upstream of the first one-way valve 21, in fact, in the situation that not considering that the first Pilot operated check valve 22 vibrates, the first Pilot operated check valve 22 also can be arranged in the downstream of the first one-way valve 21, can not exert an influence to the tune stream effect of the first damping hole 23 and/or the second damping hole 24, the counteragent of actuator still can be stablized lentamente and carry out, and guarantees the stable of hydraulic control system.
Preferably, the first Pilot operated check valve 22 is ball valve or cone valve, can ensure reverse zero leakage.
Above forward refers to the direction from bottom to top of accompanying drawing shown in Fig. 2, is oppositely direction from the top down.
The equilibrium valve 2 of the present embodiment, is particularly useful for load and fixes, to the steady and constant occasion of rate request, and the counterweight support oil cylinder of for example hoist.
In conjunction with referring to Fig. 3, according to second embodiment of the present utility model, a kind of equilibrium valve 2 is provided, comprise the first one-way valve 21, the first damping hole 23, the first Pilot operated check valve 22, the second one-way valve 26 and the second Pilot operated check valve 25, wherein the first end of the first damping hole 23 is communicated with the filler opening of the first one-way valve 21, the second end of the first damping hole 23 is communicated with the oil outlet of the first one-way valve 21, the first Pilot operated check valve 22 is communicated with the first one-way valve 21 and the first damping hole 23 respectively, the first damping hole 23 in parallel with the first one-way valve 21 after, parallel pipeline is connected with the first Pilot operated check valve 22, the second one-way valve 26 is communicated with the second Pilot operated check valve 25, and the second Pilot operated check valve 25 and the first Pilot operated check valve 22 form bidirectional hydraulic lock.In the time that hydraulic oil flows to C2 mouth from the V2 mouth of equilibrium valve 2, the second one-way valve 26 conductings, the second Pilot operated check valve 25 forward conductions, oppositely not conducting, the first Pilot operated check valve 22 reverse-conductings simultaneously, hydraulic oil flows to V1 mouth from the C1 mouth of equilibrium valve 2, due to the first one-way valve 21 not conductings, hydraulic oil can only flow to the first damping hole 23, flow to the first Pilot operated check valve 22 from the first damping hole 23, bring into play the throttle grverning effect of the first damping hole 23, make the slow in one's movements steady of actuator, can not impact hydraulic control system.
Preferably, equilibrium valve 2 is board mounting structure, can be directly installed in actuator, is simple and easy to dismounting.
Preferably, equilibrium valve 2 also comprises the second damping hole 24, the first end of the second damping hole 24 is communicated with the filler opening of the first one-way valve 21, the second end of the second damping hole 24 is communicated with the oil outlet of the first one-way valve 21, the first damping hole 23, the second damping hole 24 and the first one-way valve 21 are parallel with one another, and the first Pilot operated check valve 22 is communicated with parallel pipeline.The second damping hole 24 is adjustable damping hole, can select according to actual needs to open or close, and also can select as required the aperture of opening simultaneously.The second damping hole 24 can be, just to open in the time that the first damping hole 23 stops up in normally off as the spare unit of the first damping hole 23, guarantees the Flow-rate adjustment effect of hydraulic control system; Also can be the accessory as the first damping hole 23, can not meet while adjusting stream needs and the first damping hole 23 is opened at the first damping hole 23 simultaneously, meet better the Flow-rate adjustment requirement of system.
Preferably, equilibrium valve 2 also comprises that the first end of the 3rd damping hole 27, the three damping holes 27 is communicated with the filler opening of the second one-way valve 26, and the second end of the 3rd damping hole 27 is communicated with the oil outlet of the second one-way valve 26.Equilibrium valve 2 has two kinds of working staties, the first is that hydraulic oil flows to C1 mouth from the V1 mouth of equilibrium valve 2, hydraulic oil flows to V2 mouth from the C2 mouth of equilibrium valve 2 simultaneously, drive actuator's positive action, these state first Pilot operated check valve 22 forward conductions, oppositely not conducting, the first one-way valve 21 conductings, the second one-way valve 26 not conductings, the second Pilot operated check valve 25 reverse-conductings, because the first damping hole 23 resistances are excessive, hydraulic oil is made a slip of the tongue journey flowing to C1 from V1 mouth, to flow through from the first one-way valve 21, and due to the second one-way valve 26 not conductings, hydraulic oil is made a slip of the tongue journey flowing to V2 from C2 mouth, to flow through from the 3rd damping hole 27, the 3rd damping hole 27 is brought into play throttle grverning effect, actuator slow in one's movements, speed is steady, under the second working state, hydraulic oil flows to C2 mouth from the V2 mouth of equilibrium valve 2, hydraulic oil flows to V1 mouth from the C1 mouth of equilibrium valve 2 simultaneously, drive actuator's counteragent, now the second Pilot operated check valve 25 forward conductions, oppositely not conducting, the second one-way valve 26 conductings, the first one-way valve 21 not conductings, the first Pilot operated check valve 22 reverse-conductings, hydraulic oil is made a slip of the tongue journey flowing to C2 from V2 mouth, all flow through from the second one-way valve 26, can be through the 3rd damping hole 27, simultaneously hydraulic oil is made a slip of the tongue journey flowing to V1 from C1 mouth, all flow through from the first damping hole 23, cannot be through the first one-way valve 21, the first damping hole 23 is brought into play throttle grverning effect, actuator slow in one's movements, speed is steady.
Here the first damping hole 23 and the 3rd damping hole 27 sizes can be identical, also can be different, specifically should determine according to required actuator's motion speed.
Preferably, equilibrium valve 2 also comprises the 4th damping hole 28, the first end of the 4th damping hole 28 is communicated with the filler opening of the second one-way valve 26, the second end of the 4th damping hole 28 is communicated with the oil outlet of the second one-way valve 26, the 3rd damping hole 27, the 4th damping hole 28 and the second one-way valve 26 are parallel with one another, and the second Pilot operated check valve 25 is communicated with parallel pipeline.The 4th damping hole 28 is adjustable damping hole, can select according to actual needs to open or close, and also can select as required the aperture of opening simultaneously.The 4th damping hole 28 can be, just to open in the time that the 3rd damping hole 27 stops up in normally off as the spare unit of the 3rd damping hole 27, guarantees the Flow-rate adjustment effect of hydraulic control system; Also can be the accessory as the 3rd damping hole 27, can not meet while adjusting stream needs and the 3rd damping hole 27 is opened at the 3rd damping hole 27 simultaneously, meet better the Flow-rate adjustment requirement of system.
Preferably, the first Pilot operated check valve 22 is positioned at the upstream of the first one-way valve 21, the first Pilot operated check valve 22 is communicated with filler opening, the first end of the first damping hole 23 and the first end of the second damping hole 24 of the first one-way valve 21 respectively, the second Pilot operated check valve 25 is positioned at the upstream of the second one-way valve 26 simultaneously, and the second Pilot operated check valve 25 is communicated with filler opening, the first end of the 3rd damping hole 27 and the first end of the 4th damping hole 28 of the second one-way valve 26 respectively.With the first Pilot operated check valve 22 is arranged in to the downstream of the first one-way valve 21, the second Pilot operated check valve 25 is arranged in to the downstream comparison of the second one-way valve 26; by the first Pilot operated check valve 22 be arranged in the upstream of the first one-way valve 21, the upstream that simultaneously the second Pilot operated check valve 25 is arranged in to the second one-way valve 26 be can ensure actuator's action time; can there is not dither in the first Pilot operated check valve 22 and the second Pilot operated check valve 25, effectively protect the first Pilot operated check valve 22 and the second Pilot operated check valve 25.
Certainly, this does not also mean that the first Pilot operated check valve 22 and the second Pilot operated check valve 25 can only be arranged in respectively the upstream of the first one-way valve 21 and the second one-way valve 26, in fact, in the situation that not considering that the first Pilot operated check valve 22 and the second Pilot operated check valve 25 vibrate, the first Pilot operated check valve 22 also can be arranged in the downstream of the first one-way valve 21, the second Pilot operated check valve 25 is arranged in the downstream of the second one-way valve 26 simultaneously, can be to the first damping hole 23, the second damping hole 24, the tune stream effect of the 3rd damping hole 27 and the 4th damping hole 28 exerts an influence, the action of actuator still can be stablized lentamente and carry out, guarantee the stable of hydraulic control system.
Preferably, the first Pilot operated check valve 22 is ball valve or cone valve, and the second Pilot operated check valve 25 is ball valve or cone valve, can ensure reverse zero leakage.
Above forward refers to the direction from bottom to top of accompanying drawing shown in Fig. 3, is oppositely direction from the top down.
The equilibrium valve 2 of the present embodiment, is particularly useful for the two-way locking function that has, and the load occasion of fixing, require speed to operate steadily, the vertical support oil cylinder of for example hoist.
In conjunction with referring to Fig. 4, the invention also discloses a kind of counterweight oil cylinder hydraulic control system, comprise weight balancing oil cylinder 1, equilibrium valve 2, selector valve 3 and [constant 4, wherein equilibrium valve 2 is the equilibrium valve 2 shown in first embodiment, the C1 mouth of equilibrium valve 2 is communicated with the rodless cavity 12 of weight balancing oil cylinder 1, the V1 mouth of equilibrium valve 2 is communicated with the first actuator port A of selector valve 3, the control port C2 of the first Pilot operated check valve 22 is communicated with the second actuator port B of selector valve 3, and the second actuator port of selector valve 3 is also communicated with the rod chamber 11 of weight balancing oil cylinder 1.
As a preferred implementation, the first Pilot operated check valve 22 in equilibrium valve 2 is positioned at the upstream of the first one-way valve 21, the first Pilot operated check valve 22 is communicated with the first actuator port A of selector valve 3, and the oil outlet of the first one-way valve 21 is communicated with the rodless cavity 12 of weight balancing oil cylinder 1.
Illustrate the working principle of weight balancing oil cylinder 1 hydraulic control system below in conjunction with this preferred implementation.
1, need to promote counterweight time, selector valve 3 right side electromagnet obtain electric, selector valve 3 is in the first working position (being the right position shown in Fig. 4), the oil inlet P of selector valve 3 is communicated with the first actuator port A, the oil return inlet T of selector valve 3 is communicated with the second actuator port B, and hydraulic oil flows into the V1 mouth of equilibrium valve 2 from [constant 4 flows out through the oil inlet P of selector valve 3 and the first actuator port A; In equilibrium valve 2, hydraulic oil flows out the C1 mouth of equilibrium valve 2 successively after the first Pilot operated check valve 22 and the first one-way valve 21, then flow into the rodless cavity 12 of weight balancing oil cylinder 1, because the resistance of the first damping hole 23 is excessive, hydraulic oil first damping hole 23 of can flowing through hardly, but all flow through from the first one-way valve 21, hydraulic oil in the rod chamber 11 of weight balancing oil cylinder 1 flows into the second actuator port B of selector valve 3 simultaneously, and finally flow out from the oil return inlet T of selector valve 3, complete weight balancing oil cylinder 1 forward extend action.
2, need to lock weight balancing oil cylinder 1 time, selector valve 3 dead electricity, selector valve 3 is got back to the meta shown in Fig. 4, weight balancing oil cylinder 1 stop motion, weight balancing oil cylinder 1 hydraulic control system is in locking state.
3, need to fall counterweight time, selector valve 3 left side electromagnet obtain electric, selector valve 3 is in the second working position (being the left position shown in Fig. 4), the oil inlet P of selector valve 3 is communicated with the second actuator port B, the oil return inlet T of selector valve 3 is communicated with the first actuator port A, hydraulic oil flows into respectively the control port C2 of the first Pilot operated check valve 22 and the rod chamber 11 of weight balancing oil cylinder 1 through oil inlet P and the second actuator port B of selector valve 3 from [constant 4 flows out, the control port of the first Pilot operated check valve 22 has oil pressure to make the first Pilot operated check valve 22 reverse-conductings, hydraulic oil in the rodless cavity 12 of weight balancing oil cylinder 1 enters equilibrium valve 2 through the C1 of equilibrium valve 2 mouth simultaneously, in equilibrium valve 2, hydraulic oil cannot flow out through the first one-way valve 21, can only flow through the first damping hole 23 and/or the second damping hole 24, then flow out the V1 mouth of equilibrium valve 2 through the first Pilot operated check valve 22, flow into selector valve 3 from the first actuator port A again, and finally flow out from oil return inlet T, complete the reverse retract action of weight balancing oil cylinder 1.In this process, the first damping hole 23 and/or the second damping hole 24 are brought into play throttle grverning effect, guarantee that the slow, stable of weight balancing oil cylinder 1 retract action carries out, avoid hydraulic control system that vibration by a relatively large margin occurs and cause each parts damages, improve the Security of hydraulic control system entirety.
The utility model also provides a kind of vertical support oil cylinder hydraulic control system, comprises equilibrium valve 2, and wherein equilibrium valve 2 is second equilibrium valve 2 shown in embodiment.
As can be seen from the above description, the utility model the above embodiments have realized following technique effect:
1, adopt unidirectional damping hole, guarantee that actuator's forward moves fast, oppositely steadily declines, and meets the job requirements of specific occasion (as weight balancing oil cylinder).
2, adopt Pilot operated check valve, ensure reliable at an arbitrary position locked load.
3, increase can open and close, adjustable for subsequent use/Auxiliary Damping hole, guarantee hydraulic control system reliability of operation.
4, Pilot operated check valve is positioned at the upstream of one-way valve and damping hole, ensures Pilot operated check valve normal operation, can not occur to vibrate by a relatively large margin.
5, the component structure simple (Pilot operated check valve, one-way valve and damping hole) of selecting in equilibrium valve, manufacturing cost is lower.
The foregoing is only preferred embodiment of the present utility model, be not limited to the utility model, for a person skilled in the art, the utility model can have various modifications and variations.All within spirit of the present utility model and principle, any amendment of doing, be equal to replacement, improvement etc., within all should being included in protection domain of the present utility model.
Claims (10)
1. an equilibrium valve, is characterized in that, comprising:
The first one-way valve (21);
The first damping hole (23), the first end of described the first damping hole (23) is communicated with the filler opening of described the first one-way valve (21), and the second end of described the first damping hole (23) is communicated with the oil outlet of described the first one-way valve (21); And
The first Pilot operated check valve (22), described the first Pilot operated check valve (22) is communicated with described the first one-way valve (21) and described the first damping hole (23) respectively;
Under the state of described the first one-way valve (21) conducting, the control port oil pressure of described the first Pilot operated check valve (22) is zero, hydraulic oil flow through described the first one-way valve (21) and described the first Pilot operated check valve (22);
Under the state of not conducting of described the first one-way valve (21), the control port of described the first Pilot operated check valve (22) has oil pressure, hydraulic oil flow through described the first damping hole (23) and described the first Pilot operated check valve (22).
2. equilibrium valve according to claim 1, it is characterized in that, described equilibrium valve also comprises the second damping hole to be opened/closed (24), the first end of described the second damping hole (24) is communicated with the described filler opening of described the first one-way valve (21), and the second end of described the second damping hole (24) is communicated with the described oil outlet of described the first one-way valve (21).
3. equilibrium valve according to claim 1, it is characterized in that, described the first Pilot operated check valve (22) is communicated with the described filler opening of described the first one-way valve (21) and the described first end of described the first damping hole (23) respectively.
4. according to the equilibrium valve described in any one in claims 1 to 3, it is characterized in that, described equilibrium valve also comprises:
The second one-way valve (26); And
The second Pilot operated check valve (25), described the second Pilot operated check valve (25) is communicated with described the second one-way valve (26), and described the second Pilot operated check valve (25) and described the first Pilot operated check valve (22) form bidirectional hydraulic lock.
5. equilibrium valve according to claim 4, it is characterized in that, described equilibrium valve also comprises the 3rd damping hole (27), the first end of described the 3rd damping hole (27) is communicated with the filler opening of described the second one-way valve (26), and the second end of described the 3rd damping hole (27) is communicated with the oil outlet of described the second one-way valve (26).
6. equilibrium valve according to claim 5, it is characterized in that, described the second Pilot operated check valve (25) is communicated with the described filler opening of described the second one-way valve (26) and the described first end of described the 3rd damping hole (27) respectively.
7. equilibrium valve according to claim 5, it is characterized in that, described equilibrium valve also comprises the 4th damping hole (28) to be opened/closed, the first end of described the 4th damping hole (28) is communicated with the described filler opening of described the second one-way valve (26), and the second end of described the 4th damping hole (28) is communicated with the described oil outlet of described the second one-way valve (26).
8. a counterweight oil cylinder hydraulic control system, comprising:
Weight balancing oil cylinder (1);
Equilibrium valve (2), described equilibrium valve (2) is communicated with the rodless cavity (12) of described weight balancing oil cylinder (1); And
Selector valve (3), the first actuator port of described selector valve (3) is communicated with described equilibrium valve (2), and the second actuator port of described selector valve (3) is communicated with the rod chamber (11) of described weight balancing oil cylinder (1);
It is characterized in that, described equilibrium valve (2) is the equilibrium valve described in claim 1 or 2, and the described control port of described the first Pilot operated check valve (22) is communicated with described second actuator port of described selector valve (3).
9. a counterweight oil cylinder hydraulic control system, comprising:
Weight balancing oil cylinder (1);
Equilibrium valve (2), described equilibrium valve (2) is communicated with the rodless cavity (12) of described weight balancing oil cylinder (1); And
Selector valve (3), the first actuator port of described selector valve (3) is communicated with described equilibrium valve (2), and the second actuator port of described selector valve (3) is communicated with the rod chamber (11) of described weight balancing oil cylinder (1);
It is characterized in that, described equilibrium valve (2) is equilibrium valve claimed in claim 3, described first actuator port of described selector valve (3) is communicated with described the first Pilot operated check valve (22), the described oil outlet of described the first one-way valve (21) is communicated with the rodless cavity (12) of described weight balancing oil cylinder (1), and the described control port of described the first Pilot operated check valve (22) is communicated with described second actuator port of described selector valve (3).
10. a vertical support oil cylinder hydraulic control system, comprises equilibrium valve (2), it is characterized in that, described equilibrium valve (2) is the equilibrium valve described in any one in claim 4 to 7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420272138.2U CN203879835U (en) | 2014-05-26 | 2014-05-26 | Balance valve, counterweight oil cylinder hydraulic control system and vertical support leg oil cylinder hydraulic control system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420272138.2U CN203879835U (en) | 2014-05-26 | 2014-05-26 | Balance valve, counterweight oil cylinder hydraulic control system and vertical support leg oil cylinder hydraulic control system |
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| Publication Number | Publication Date |
|---|---|
| CN203879835U true CN203879835U (en) | 2014-10-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420272138.2U Expired - Lifetime CN203879835U (en) | 2014-05-26 | 2014-05-26 | Balance valve, counterweight oil cylinder hydraulic control system and vertical support leg oil cylinder hydraulic control system |
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| Country | Link |
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| CN (1) | CN203879835U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104528550A (en) * | 2014-12-03 | 2015-04-22 | 中联重科股份有限公司 | Crane counterweight lifting system |
| CN108439219A (en) * | 2018-06-13 | 2018-08-24 | 江苏建筑职业技术学院 | Can automatic identification weight balance weight system and control method |
| CN114412851A (en) * | 2021-12-30 | 2022-04-29 | 湖南中联重科应急装备有限公司 | Vertical supporting leg hydraulic system and engineering vehicle |
-
2014
- 2014-05-26 CN CN201420272138.2U patent/CN203879835U/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104528550A (en) * | 2014-12-03 | 2015-04-22 | 中联重科股份有限公司 | Crane counterweight lifting system |
| CN104528550B (en) * | 2014-12-03 | 2016-05-11 | 中联重科股份有限公司 | Crane counterweight lifting system |
| CN108439219A (en) * | 2018-06-13 | 2018-08-24 | 江苏建筑职业技术学院 | Can automatic identification weight balance weight system and control method |
| CN114412851A (en) * | 2021-12-30 | 2022-04-29 | 湖南中联重科应急装备有限公司 | Vertical supporting leg hydraulic system and engineering vehicle |
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Granted publication date: 20141015 |