CN103790889B - Oiling valve block and complex controll flow multi-way valve - Google Patents
Oiling valve block and complex controll flow multi-way valve Download PDFInfo
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- CN103790889B CN103790889B CN201410084394.3A CN201410084394A CN103790889B CN 103790889 B CN103790889 B CN 103790889B CN 201410084394 A CN201410084394 A CN 201410084394A CN 103790889 B CN103790889 B CN 103790889B
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Abstract
The invention provides a kind of oiling valve block and complex controll flow multi-way valve, belong to technical field of hydraulic pressure.It solve the problem that existing multi-way valve also exists poor universality.This oiling valve block comprises oil-feed valve body, has the first load-sensitive chamber and minus flow feedback cavity in oil-feed valve body, oil-feed valve body also has the load-sensitive interface be connected with the first load-sensitive chamber and the minus flow feedback interface be connected with minus flow feedback cavity; Be connected by throttle valve between minus flow feedback cavity and oil back chamber or be directly connected; The control structure whether be communicated with minus flow feedback cavity with the first load-sensitive chamber oil pressure cntrol oil suction chamber according to oil suction chamber oil pressure is provided with in oil-feed valve body.A kind of complex controll flow multi-way valve comprises at least two pieces of operating valve blocks, scavenger valve block and above-mentioned oiling valve block; This complex controll flow multi-way valve adopts downstream pressure to compensate, and have the saturated function of anti-current amount, namely when flow system flow is inadequate, each executive component flow also can be pro rata distributed.
Description
Technical field
The invention belongs to technical field of hydraulic pressure, relate to a kind of hydraulic control valve, particularly a kind of oiling valve block.
The invention belongs to technical field of hydraulic pressure, relate to a kind of multi-way valve, particularly a kind of complex controll flow multi-way valve.
Background technique
Multi-way valve adopts unified modular design, can provide reliable system scheme for the manufacturer of engineering vehicle.User carries out different combinations according to functional requirement to valve body, simple and reliable.Thus multi-way valve all has application in fields such as excavator, small sized loader, loader-digger, rig, fork truck, ore deposit machine, agricultural machinery.
At present, hydraulic system engineering machinery used is quantitative system, minus flow system or load sensitive system mainly.And existing multi-way valve is all only applicable to a kind of hydraulic system in above-mentioned quantitative system, minus flow system or load sensitive system.As everyone knows, present construction machinery product model is numerous, and different models may adopt different hydraulic systems completely; In other words, existing multi-way valve also exists the problem of poor universality.
Summary of the invention
The object of the invention is to there are the problems referred to above for existing technology, propose a kind of oiling valve block, the technical problem to be solved in the present invention how to improve the versatility of oiling valve block.
The invention allows for a kind of complex controll flow multi-way valve with above-mentioned oiling valve block, the technical problem to be solved in the present invention how to improve the versatility of multi-way valve.
Object of the present invention realizes by following technical proposal: a kind of oiling valve block, comprise oil-feed valve body, there is oil suction chamber and oil back chamber, oil return interface oil-feed valve body having the oil-feed interface be connected with oil suction chamber, the oil outlet be connected with oil suction chamber and be connected with oil back chamber in oil-feed valve body; It is characterized in that also there is in oil-feed valve body the first load-sensitive chamber and minus flow feedback cavity, oil-feed valve body also has the load-sensitive interface be connected with the first load-sensitive chamber and the minus flow feedback interface be connected with minus flow feedback cavity; Be connected by throttle valve between minus flow feedback cavity and oil back chamber or be directly connected; The control structure whether be communicated with minus flow feedback cavity with the first load-sensitive chamber oil pressure cntrol oil suction chamber according to oil suction chamber oil pressure is provided with in oil-feed valve body.
The oiling valve block of said structure is applicable to being applied in minus flow system, and minus flow feedback interface is connected with the corresponding interface of minus flow pump; Load-sensitive interface adopts the shutoff of bolt plug.Adopt bolt plug by load-sensitive interface and the equal shutoff of minus flow feedback interface when being applied in quantitative system by this oiling valve block; And removal throttle valve makes between minus flow feedback cavity and oil back chamber straight-through.When being applied in load sensitive system by this oiling valve block, adopt bolt plug by the shutoff of minus flow feedback interface; And removal throttle valve makes between minus flow feedback cavity and oil back chamber straight-through.
In above-mentioned oiling valve block, described control structure comprises off-load spool, the valve core channel be all connected with minus flow feedback cavity with oil suction chamber, the first load-sensitive chamber is offered in oil-feed valve body, off-load spool is positioned at valve core channel, the first spring is provided with in first load-sensitive chamber, first spring one end and off-load spool lean, and the first spring the other end and oil-feed valve body lean.Promote off-load spool to move along valve core channel inwall when oil suction chamber oil pressure raises, oil suction chamber is connected with minus flow feedback cavity.Also can promote off-load spool when the first load-sensitive chamber oil pressure raises to move along valve core channel inwall, make oil suction chamber and minus flow feedback cavity switch to cut-off state from connected state.
In above-mentioned oiling valve block, have guide slide in described oil-feed valve body, be provided with spring in described guide slide against block, spring is connected against block outer side surface with guide slide inner wall sealing, and the described first spring the other end and spring lean against block one end face; Described oil-feed valve body is connected with the adjusting bolt leant against block other end with spring.Obviously, the first spring the other end is leant against block and adjusting bolt and oil-feed valve body by spring; By screwing the position of adjusting bolt Regulation spring against block, change the default elastic force of the first spring; And then change the oil pressure of the oil suction chamber when oil suction chamber is connected with minus flow feedback cavity.
In above-mentioned oiling valve block, described throttle valve comprises the throttling valve core with throttle orifice, oil-feed valve body has the first sealing lip, has the second sealing lip outside the throttle orifice of throttling valve core; Be provided with the second spring between described throttling valve core and oil-feed valve body, the second spring one end and throttling valve core lean, and the other end and oil-feed valve body lean.When fluid is greater than the default value of elastic of the second spring by the choke pressure that throttle valve produces, the second sealing lip departs from the first sealing lip, and throttle valve is all opened, and realizes overflow, protects pump and reduces the loss.When the oil pressure in minus flow feedback cavity is less than the default value of elastic of the second spring, throttling valve core is under the elastic force effect of the second spring, and the second sealing lip and the first sealing lip lean and formed and seal.
Conveniently load and unload throttle valve, in above-mentioned oiling valve block, described oil-feed valve body has handling hole, and described handling hole is provided with bolt plug.
A kind of complex controll flow multi-way valve, is characterized in that, comprise at least two pieces of operating valve blocks, scavenger valve block and above-mentioned oiling valve block; Operating valve block has oil inlet passage, the first oil duct, the second oil duct and drainback passage; Also there is in operating valve block the load-sensitive oil duct be connected with the second oil duct; Be provided with the selector valve core structure that can control oil inlet passage and the first oil duct connected state in operating valve block and the first oil duct and the second oil duct connected state can be controlled and there is the pressure compensation valve core structure in the second load-sensitive chamber; Selector valve core structure also comprises the load-sensitive chamber pressure release oil duct that the second oil duct can be made to be connected with drainback passage; The oil inlet passage of all working valve block is all connected with the oil outlet of oiling valve block; The load-sensitive oil duct of all working valve block makes the load-sensitive oil duct that in all load-sensitive oil ducts, oil pressure is the highest be connected with the first load-sensitive chamber by shuttle valve oil pressure comparative structure; Second load-sensitive chamber of all working valve block is all connected with the first load-sensitive chamber.
When the quantity of operating valve block is two pieces, in above-mentioned complex controll flow multi-way valve, described shuttle valve oil pressure comparative structure comprises one group of shuttle valve, shuttle valve has two oil pressure ratios comparatively interface and external interface, external interface is connected with the first load-sensitive chamber, and two oil pressure ratios are connected with the load-sensitive oil duct of two pieces of operating valve blocks respectively correspondingly compared with interface.
When the quantity of operating valve block is for being greater than two pieces, in above-mentioned complex controll flow multi-way valve, described shuttle valve oil pressure comparative structure comprises array shuttle valve, is provided with one group of shuttle valve between adjacent two pieces of operating valve blocks; Shuttle valve has two oil pressure ratios comparatively interface and external interface; All shuttle valves are connected in series, and two oil pressure ratios being positioned at the shuttle valve of one end are connected with the load-sensitive oil duct of two pieces of adjacent operating valve blocks accordingly respectively correspondingly compared with interface, and an oil pressure ratio of external interface and adjacent shuttle valve comparatively interface is connected; The oil pressure ratio being positioned at the shuttle valve of the other end compared with interface and adjacent shuttle valve an oil pressure ratio comparatively interface be connected, another oil pressure ratio is connected with the load-sensitive oil duct of an operating valve block compared with interface, and the external interface being positioned at the shuttle valve of the other end is connected with the first load-sensitive chamber.
In above-mentioned complex controll flow multi-way valve, described selector valve core structure comprises changeover valve core, changeover valve core has the oil-feed circular groove corresponding with oil inlet passage position and the first fuel-displaced circular groove corresponding with the first oil duct position, changeover valve core outer side surface also has the throttling groove between oil-feed circular groove and the first fuel-displaced circular groove; Pressure release oil duct in load-sensitive chamber is positioned at changeover valve core.
In above-mentioned complex controll flow multi-way valve, described pressure compensation valve core structure comprises pressure compensation spool peace weighing apparatus chamber, what pressure-compensated valve in-core had connection first oil duct and a counter balance pocket is communicated with oil duct, is provided with the 3rd spring making pressure compensation spool have compression counter balance pocket trend all the time in described second load-sensitive chamber.
In above-mentioned complex controll flow multi-way valve, there are between described second oil duct and the first oil duct two connecting ports.Second oil duct forms Twin channel oil duct at valve inner, and peak rate of flow is higher, makes along stroke pressure loss less.
Compared with prior art, this complex controll flow multi-way valve adopts downstream pressure to compensate, and have the saturated function of anti-current amount, namely when flow system flow is inadequate, each executive component flow also can be pro rata distributed.
This oiling valve block and this complex controll flow multi-way valve are by selecting to install corresponding module and regulate the force value of the first spring to realize being applied on quantitative system, minus flow system or load sensitive system.
Accompanying drawing explanation
Fig. 1 is the sectional structure schematic diagram of this oiling valve block.
Fig. 2 is the sectional view of A-A in Fig. 1.
Fig. 3 is the hydraulic schematic diagram that this complex controll flow multi-way valve is applied in the load sensitive system of embodiment one.
Fig. 4 is the structural representation of this complex controll flow multi-way valve embodiment one.
Fig. 5 is the sectional structure schematic diagram that operating valve block is in closed condition.
Fig. 6 is the sectional structure schematic diagram of shuttle valve oil pressure comparative structure in embodiment one.
Fig. 7 is the sectional structure schematic diagram that operating valve block is in open mode.
Fig. 8 is the sectional structure schematic diagram that this oiling valve block is in another state.
Fig. 9 is the sectional structure schematic diagram that this oiling valve block is applied in the load sensitive system of embodiment one.
Figure 10 is the sectional structure schematic diagram of scavenger valve block.
Figure 11 is the hydraulic schematic diagram that this complex controll flow multi-way valve is applied in the minus flow system of embodiment four.
Figure 12 is the sectional structure schematic diagram that this oiling valve block is applied in the minus flow system of embodiment four.
Figure 13 is the sectional structure schematic diagram that this oiling valve block is applied in the quantitative system of embodiment three.
Figure 14 is the hydraulic schematic diagram of this complex controll flow multi-way valve embodiment two.
Figure 15 is the structural representation of this complex controll flow multi-way valve embodiment two.
Figure 16 is the sectional structure schematic diagram of shuttle valve oil pressure comparative structure in embodiment two.
Figure 17 is the hydraulic schematic diagram that this complex controll flow multi-way valve is applied in the quantitative system of embodiment three.
In figure, 1, oiling valve block; 1a, oil-feed valve body; 1b, throttle valve; 1b1, throttling valve core; 1b2, the second spring; 1c, oil suction chamber; 1d, oil back chamber; 1e, the first load-sensitive chamber; 1f, minus flow feedback cavity; 1g, oil outlet; 1h, off-load spool; 1i, the first spring; 1j, guide slide; 1k, spring are against block; 1m, adjusting bolt; 1n, bolt plug; P1, oil-feed interface; T1, oil return interface; LS, load-sensitive interface; FK, minus flow feedback interface; 2, operating valve block; 2a, oil inlet passage; 2b, the first oil duct; 2c, the second oil duct; 2d, drainback passage; 2e, working hole; 2f, changeover valve core; 2g, throttling groove; 2h, load-sensitive oil duct; 2i, load-sensitive chamber pressure release oil duct; 2j, pressure compensation spool; 2k, the second load-sensitive chamber; 2m, connection oil duct; 2n, the 3rd spring; 3, scavenger valve block; 4, shuttle valve; 5, the first relief valve; 6, the second relief valve.
Embodiment
Be below specific embodiments of the invention and by reference to the accompanying drawings, technological scheme of the present invention is further described, but the present invention be not limited to these embodiments.
Embodiment one
As depicted in figs. 1 and 2, this oiling valve block 1 comprises oil-feed valve body 1a, throttle valve 1b and control structure.
There is in oil-feed valve body 1a oil suction chamber 1c, oil back chamber 1d, the first load-sensitive chamber 1e and minus flow feedback cavity 1f.Oil-feed valve body 1a has the oil-feed interface P1 be connected with oil suction chamber 1c, the oil outlet 1g be connected with oil suction chamber 1c, the oil return interface T1 be connected with oil back chamber 1d, the load-sensitive interface LS be connected with the first load-sensitive chamber 1e and the minus flow feedback interface FK be connected with minus flow feedback cavity 1f.Specifically, minus flow feedback cavity 1f is between oil suction chamber 1c and the first load-sensitive chamber 1e, and whether this layout is more conducive to control structure and is communicated with minus flow feedback cavity 1f with the first load-sensitive chamber 1e oil pressure cntrol oil suction chamber 1c according to oil suction chamber 1c oil pressure; In other words, this layout have reasonable in design, make structure simpler and manipulate advantage more easily.
Control structure comprises off-load spool 1h, the valve core channel be all connected with minus flow feedback cavity 1f with oil suction chamber 1c, the first load-sensitive chamber 1e is offered in oil-feed valve body 1a, off-load spool 1h is positioned at valve core channel, the first spring 1i is provided with in first load-sensitive chamber 1e, first spring 1i one end and off-load spool 1h lean, and the first spring 1i the other end and oil-feed valve body 1a lean.As shown in Figure 1, off-load spool 1h is under the effect of the first spring 1i, and left end and the oil-feed valve body 1a of off-load spool 1h lean, and off-load spool 1h makes oil suction chamber 1c and the first load-sensitive chamber 1e be in cut-off state.As depicted in figure 8, off-load spool 1h moves to the right, and the first spring 1i is compressed, and oil suction chamber 1c and the first load-sensitive chamber 1e is in connected state.
As shown in Figure 1, as further improvement, in oil-feed valve body 1a, have guide slide 1j, be provided with spring against block 1k in guide slide 1j, the first spring 1i the other end and spring lean against block 1k mono-end face; Oil-feed valve body 1a is connected with the adjusting bolt 1m leant against block 1k other end with spring; Obviously, the first spring 1i the other end is leant against block 1k and adjusting bolt 1m and oil-feed valve body 1a by spring.The default elastic force of the first spring 1i is changed by screwing adjusting bolt 1m; And then change the oil pressure of the oil suction chamber 1c when oil suction chamber 1c is connected with minus flow feedback cavity 1f; This oiling valve block 1 is made to mate more suitably from different hydraulic systems thus.In other words, the versatility that said structure ensure that oil-feed valve body 1a is effectively set.Spring is connected against block 1k outer side surface with guide slide 1j inner wall sealing, and specifically, spring has annular seal groove on block 1k outer side surface, has seal ring in annular seal groove inner sleeve.Above-mentioned sealing configuration ensures that spring can slide against block 1k effectively, and hydraulic oil can be avoided again to reveal.
As shown in Figure 2, be connected by throttle valve 1b between minus flow feedback cavity 1f and oil back chamber 1d.As shown in Figure 12 and Figure 13, be directly connected between minus flow feedback cavity 1f and oil back chamber 1d.Throttle valve 1b comprises the throttling valve core 1b1 with throttle orifice, oil-feed valve body 1a has the first sealing lip, has the second sealing lip outside the throttle orifice of throttling valve core 1b1; Be provided with the second spring 1b2 between described throttling valve core 1b1 and oil-feed valve body 1a, second spring 1b2 one end and throttling valve core 1b1 lean, and the other end and oil-feed valve body 1a lean.When fluid is greater than the default value of elastic of the second spring 1b2 by the choke pressure that throttle valve 1b produces, the second sealing lip departs from the first sealing lip, and throttle valve 1b all opens, and realizes overflow, protects pump and reduces the loss.
Conveniently load and unload throttle valve 1b, oil-feed valve body 1a has handling hole, and handling hole is provided with bolt plug 1n.Bolt plug 1n is provided with pilot hole, and throttling valve core 1b1 is cylindrical, and throttling valve core 1b1 penetrates in pilot hole, just moves along pilot hole sidewall when throttling valve core 1b1 moves; Can the second spring 1b2 be arranged in throttling valve core 1b1 and pilot hole simultaneously, ensure structural compactness; Effectively improve the stability of throttling valve core 1b1 movement, and then ensure the stability of throttle valve 1b.
As shown in Figures 3 to 6, this complex controll flow multi-way valve comprises two pieces of operating valve blocks, 2, one piece of scavenger valve block 3 and one piece of above-mentioned oiling valve block 1; Fold by oiling valve block 1, operating valve block 2, operating valve block 2 and scavenger valve block 3 order successively from side to opposite side and establish.
As shown in Figure 5, operating valve block 2 has oil inlet passage 2a, the first oil duct 2b, the second oil duct 2c, a drainback passage 2d and two working hole 2e.The selector valve core structure that can control oil inlet passage 2a and the first oil duct 2b connected state and the pressure compensation valve core structure that can control the first oil duct 2b and the second oil duct 2c connected state is equipped with in operating valve block 2.
Selector valve core structure comprises changeover valve core 2f, changeover valve core 2f has the oil-feed circular groove corresponding with oil inlet passage 2a position, with corresponding the first fuel-displaced circular groove in the first oil duct 2b position and with two working hole 2e positions the second fuel-displaced circular groove one to one.Changeover valve core 2f outer side surface also has the throttling groove 2g between oil-feed circular groove and the first fuel-displaced circular groove.
Also there is in operating valve block 2 the load-sensitive oil duct 2h be connected with the second oil duct 2c; An energy load-sensitive chamber pressure release oil duct 2i is offered in changeover valve core 2f; When the first oil duct 2b and the second oil duct 2c is in cut-off state, load-sensitive chamber pressure release oil duct 2i makes the second oil duct 2c be connected with drainback passage 2d; When the first oil duct 2b and the second oil duct 2c is in connected state, load-sensitive chamber pressure release oil duct 2i is in cut-off state, and namely the fluid of the second oil duct 2c cannot be entered in drainback passage 2d by load-sensitive chamber pressure release oil duct 2i.
Pressure compensation valve core structure comprises pressure compensation spool 2j, counter balance pocket and the second load-sensitive chamber 2k.Specifically, pressure compensation spool 2j is arranged in the valve body of operating valve block 2, forms counter balance pocket and the second load-sensitive chamber 2k between the two ends of pressure compensation spool 2j and the valve body of operating valve block 2.What pressure compensation spool 2j offers connection first oil duct 2b and counter balance pocket is communicated with oil duct 2m.The 3rd spring 2n making pressure compensation spool 2j have compression counter balance pocket trend is all the time provided with in second load-sensitive chamber 2k.As shown in Figure 5, pressure compensation spool 2j makes the second oil duct 2c and the first oil duct 2b be in cut-off state.As shown in Figure 7, the second oil duct 2c and the first oil duct 2b is in connected state.
As shown in Figure 5, the second oil duct 2c is U-shaped, has two connecting ports between the second oil duct 2c and the first oil duct 2b.When the second oil duct 2c and the first oil duct 2b is in connected state, two connecting ports are higher relative to a connecting port peak rate of flow, and then make along stroke pressure loss less.
As shown in Fig. 3, Figure 11 to Figure 14, the oil inlet passage 2a of all working valve block 2 is all connected with the oil outlet 1g of oiling valve block 1.Second load-sensitive chamber 2k of all working valve block 2 is all connected with the first load-sensitive chamber 1e.The load-sensitive oil duct 2h of all working valve block 2 makes the load-sensitive oil duct 2h that in all load-sensitive oil duct 2h, oil pressure is the highest be connected with the first load-sensitive chamber 1e by shuttle valve oil pressure comparative structure.
As shown in Figure 6, shuttle valve oil pressure comparative structure comprises one group of shuttle valve 4, shuttle valve 4 has two oil pressure ratios comparatively interface and external interface, external interface is connected with the first load-sensitive chamber 1e, and two oil pressure ratios are connected with the load-sensitive oil duct 2h of two pieces of operating valve blocks 2 respectively correspondingly compared with interface.
As shown in Fig. 3, Figure 11 to Figure 14, the operating valve block 2 of close scavenger valve block 3 is for Control Engineering machinery rotation.As shown in Figure 10, scavenger valve block 3 is arranged the first relief valve 5 be connected with the load-sensitive oil duct 2h of the operating valve block 2 for Control Engineering machinery rotation.Engineering machinery especially excavator work time nearly 50% time in revolution, because revolution inertia ratio is comparatively large, cause revolution to start and anxious stopping time pressure ratio higher, the first relief valve 5 effectively limits rotation pressure, then effectively reduce revolution and impact.Meanwhile, during other action composite moves, avoid because revolution instantaneous pressure rises and cause its pressure reduction to become large, causing system to generate heat.
As shown in Figures 1 to 9, when this oiling valve block 1 and this complex controll flow multi-way valve are applied in load sensitive system, adopt bolt plug 1n by minus flow feedback interface FK shutoff; And removal throttle valve 1b makes between minus flow feedback cavity 1f and oil back chamber 1d straight-through.
When the changeover valve core 2f in all working valve block 2 is positioned at meta, because the load-sensitive chamber pressure release oil duct 2i in operating valve block 2 makes the second oil duct 2c be connected with drainback passage 2d, the first load-sensitive chamber 1e is connected with the second oil duct 2c with load-sensitive oil duct 2h by shuttle valve oil pressure comparative structure; Therefore the first load-sensitive chamber 1e is connected with drainback passage 2d.
Now load sensitive pump exports with the fluid of minimum discharge.Because the changeover valve core 2f in operating valve block 2 is positioned at meta, be closed to working hole 2e oil circuit, so pumping pressure raises.Form oil pressure ratio comparatively chamber between off-load spool 1h left end and oil-feed valve body 1a, off-load spool 1h left end has and is communicated with the aperture of oil pressure ratio compared with chamber and oil suction chamber 1c; Fluid arrives oil pressure ratio comparatively chamber by the aperture on off-load spool 1h, until be greater than the first spring 1i setting of off-load spool 1h right-hand member, off-load spool 1h starts to move right, and oil suction chamber 1c and oil back chamber 1d connects, until stop mobile during off-load spool 1h pressure at two ends balance.Such pump comes oilyly to realize meta off-load through off-load spool 1h to the oil return interface T1 case that deoils.
As shown in Figure 7, when the changeover valve core 2f of single operating valve block 2 is positioned at commutation position, oil inlet passage 2a is connected with the first oil duct 2b by the throttling groove 2g on changeover valve core 2f, the counter balance pocket being positioned at pressure compensation spool 2j left end is arrived again by the connection oil duct 2m on pressure compensation spool 2j, when counter balance pocket pressure is greater than the 3rd spring 2n pressure being positioned at pressure compensation spool 2j right-hand member, pressure compensation spool 2j moves right, now the first oil duct 2b is connected with the second oil duct 2c, the fluid major part of the second oil duct 2c flows to one of them working hole 2e, another working hole 2e fluid flows to drainback passage 2d.The fluid of the second oil duct 2c has sub-fraction to open shuttle valve 4 diffluence first load-sensitive chamber 1e by load-sensitive oil duct 2h.Off-load spool 1h in oiling valve block 1 moves to left under the oil pressure effect of the first spring 1i spring force and the first load-sensitive chamber 1e, disconnects the oil suction chamber 1c of oiling valve block 1 and the connection of oil back chamber 1d.Because the second load-sensitive chamber 2k of operating valve block 2 is all connected with the first load-sensitive chamber 1e of oiling valve block 1, pressure compensation spool 2j then in operating valve block 2 moves to left under the oil pressure effect of the 3rd spring 2n and the second load-sensitive chamber 2k, until pressure compensation spool 2j pressure at two ends is equal reach balance, the oil pressure that now pressure of the first oil duct 2b equals the second load-sensitive chamber 2k adds the pressure of the 3rd spring 2n, so the pressure reduction of oil inlet passage 2a and the first oil duct 2b just equals the spring setting of load-sensitive pump flow control valve, thus the flow of the first oil duct 2b is only relevant to the throttling groove 2g opening area on changeover valve core 2f.
In order to avoid the oil liquid pressure in the first load-sensitive chamber 1e is too high, in oiling valve block 1, be provided with the second relief valve 6 be connected with the first load-sensitive chamber 1e.
When the changeover valve core 2f of operating valve block 2 switches to meta from commutation position, namely switch to closed condition from operating valve block 2 from open mode.Oil inlet passage 2a and the first oil duct 2b disconnects, and pressure compensation spool 2j makes the first oil duct 2b and the second oil duct 2c disconnect under the effect of the 3rd spring 2n.Because the second load-sensitive chamber 2k and the second oil duct 2c is all connected with the first load-sensitive chamber 1e, and the second oil duct 2c is connected with drainback passage by the load-sensitive chamber pressure release oil duct 2i on changeover valve core 2f, thus release closes suddenly the residual pressure of generation due to commutation valve rod.
When two operating valve blocks 2 work simultaneously, due under the effect of shuttle valve oil pressure comparative structure, only have the highest fluid of induced pressure can arrive the first load-sensitive chamber 1e, because the second load-sensitive chamber 2k in all working valve block 2 is all directly communicated with the first load-sensitive chamber 1e, therefore the compensating spool automatic position adjusting function that induced pressure is little, the first oil duct 2b and the second oil duct 2c is made to produce pressure reduction, until the first oil duct 2b pressure equals the pressure that the second load-sensitive chamber 2k pressure adds the 3rd spring 2n.So the pressure reduction of oil inlet passage 2a and the first oil duct 2b just equals the spring setting of load-sensitive pump flow control valve during each operating valve block 2 loaded work piece, thus the flow of the first oil duct 2b is only relevant to the throttling groove 2g opening area of commutation valve rod.
Embodiment two
The present embodiment with the structure of embodiment one and principle substantially identical, different place is: as shown in Figure 14 to Figure 16, and this complex controll flow multi-way valve comprises seven pieces of operating valve blocks, 2, one piece of scavenger valve block 3 and one piece of above-mentioned oiling valve block 1; Oiling valve block 1 and scavenger valve block 3 lay respectively at both sides; In other words, establish by oiling valve block 1, first operating valve block 2, second operating valve block 2, the 3rd operating valve block 2, the 4th operating valve block 2, the 5th operating valve block 2, the 6th operating valve block 2, the 7th operating valve block 2 and scavenger valve block 3 order is folded successively from side to opposite side.
Shuttle valve oil pressure comparative structure comprises six groups of shuttle valves 4, is provided with one group of shuttle valve 4 between adjacent two pieces of operating valve blocks 2; Shuttle valve 4 has two oil pressure ratios comparatively interface and external interface; All shuttle valves 4 are connected in series.Specifically, two oil pressure ratios of the shuttle valve 4 between the 6th operating valve block 2 and the 7th operating valve block 2 are connected with the load-sensitive oil duct 2h of the 7th operating valve block 2 with the 6th operating valve block 2 respectively correspondingly compared with interface.
An oil pressure ratio of the shuttle valve 4 between the 5th operating valve block 2 and the 6th operating valve block 2 is connected compared with the external interface of interface with the shuttle valve 4 between the 6th operating valve block 2 and the 7th operating valve block 2, and another oil pressure ratio of the shuttle valve 4 between the 5th operating valve block 2 and the 6th operating valve block 2 is connected with the load-sensitive oil duct 2h of the 5th operating valve block 2 compared with interface.
From the shuttle valve 4 between the 5th operating valve block 2 and the 6th operating valve block 2 to all connecting by said structure being positioned at the shuttle valve 4 between the first operating valve block 2 and the second operating valve block 2; An oil pressure ratio of the shuttle valve 4 namely between N operating valve block 2 and N+1 operating valve block 2 is connected compared with the external interface of interface with the shuttle valve 4 between N+1 operating valve block 2 and N+2 operating valve block 2, and another oil pressure ratio of the shuttle valve 4 between N operating valve block 2 and N+1 operating valve block 2 is connected with the load-sensitive oil duct 2h of N operating valve block 2 compared with interface; And the external interface being positioned at the shuttle valve 4 of one end is connected with the first load-sensitive chamber 1e; The oil pressure ratio being positioned at the shuttle valve 4 of the other end is connected with the load-sensitive oil duct 2h of last operating valve block 2 compared with interface.
When multiple operating valve block 2 works simultaneously, due under the effect of shuttle valve oil pressure comparative structure, only have the highest fluid of induced pressure can arrive the first load-sensitive chamber 1e, because the second load-sensitive chamber 2k in all working valve block 2 is all directly communicated with the first load-sensitive chamber 1e, therefore the compensating spool automatic position adjusting function that induced pressure is little, the first oil duct 2b and the second oil duct 2c is made to produce pressure reduction, until the first oil duct 2b pressure equals the pressure that the second load-sensitive chamber 2k pressure adds the 3rd spring 2n.So the pressure reduction of oil inlet passage 2a and the first oil duct 2b just equals the spring setting of load-sensitive pump flow control valve during each operating valve block 2 loaded work piece, thus the flow of the first oil duct 2b is only relevant to the throttling groove 2g opening area of commutation valve rod.
Embodiment three
The present embodiment with the structure of embodiment one or embodiment two and principle substantially identical, different place is: as shown in Figure 13 and Figure 17, when this oiling valve block 1 and this complex controll flow multi-way valve are applied in quantitative system, adopt bolt plug 1n by load-sensitive interface LS and the equal shutoff of minus flow feedback interface FK; And removal throttle valve 1b makes between minus flow feedback cavity 1f and oil back chamber 1d straight-through.
Embodiment four
The present embodiment with the structure of embodiment one or embodiment two and principle substantially identical, different place is: as is illustrated by figs. 11 and 12, this oiling valve block 1 and this complex controll flow multi-way valve are applied in variable system, and minus flow feedback interface FK is connected with the corresponding interface of minus flow pump; Load-sensitive interface LS adopts bolt plug 1n shutoff.By the pressure reduction of the value determination operating valve block 2 oil inlet passage 2a and the first oil duct 2b that set up the first spring 1i.When the flow that pump exports is greater than the flow of system needs, the pressure reduction of operating valve block 2 oil inlet passage 2a and the first oil duct 2b is greater than spring setting, off-load spool 1h moves right, oil suction chamber 1c is connected with minus flow feedback cavity 1f, the fluid of minus flow feedback cavity 1f produces choke pressure by throttle valve 1b, choke pressure feeds back on minus flow pump by the excuse of minus flow feedback, regulates pump swash plate, flow is reduced.When fluid is greater than the second spring 1b2 setting value by the choke pressure that throttle valve 1b produces, throttle valve 1b all opens, and realizes overflow, protects pump and reduces the loss.
Claims (10)
1. an oiling valve block, comprise oil-feed valve body (1a), there is oil suction chamber (1c) and oil back chamber (1d), the oil return interface (T1) oil-feed valve body (1a) having the oil-feed interface (P1) be connected with oil suction chamber (1c), the oil outlet (1g) be connected with oil suction chamber (1c) and be connected with oil back chamber (1d) in oil-feed valve body (1a); It is characterized in that, also there is in oil-feed valve body (1a) the first load-sensitive chamber (1e) and minus flow feedback cavity (1f), oil-feed valve body (1a) also has the load-sensitive interface (LS) be connected with the first load-sensitive chamber (1e) and the minus flow feedback interface (FK) be connected with minus flow feedback cavity (1f); Be connected by throttle valve (1b) or be directly connected between minus flow feedback cavity (1f) and oil back chamber (1d); The control structure whether be communicated with minus flow feedback cavity (1f) with the first load-sensitive chamber (1e) oil pressure cntrol oil suction chamber (1c) according to oil suction chamber (1c) oil pressure is provided with in oil-feed valve body (1a).
2. oiling valve block according to claim 1, it is characterized in that, described control structure comprises off-load spool (1h), offer in oil-feed valve body (1a) and oil suction chamber (1c), the valve core channel that first load-sensitive chamber (1e) is all connected with minus flow feedback cavity (1f), off-load spool (1h) is positioned at valve core channel, the first spring (1i) is provided with in first load-sensitive chamber (1e), first spring (1i) one end and off-load spool (1h) lean, first spring (1i) the other end and oil-feed valve body (1a) lean.
3. oiling valve block according to claim 1, it is characterized in that, described control structure comprises off-load spool (1h), the valve core channel be all connected with minus flow feedback cavity (1f) with oil suction chamber (1c), the first load-sensitive chamber (1e) is offered in oil-feed valve body (1a), off-load spool (1h) is positioned at valve core channel, be provided with the first spring (1i) in first load-sensitive chamber (1e), the first spring (1i) one end and off-load spool (1h) lean; Guide slide (1j) is had in oil-feed valve body (1a), spring is provided with against block (1k) in described guide slide (1j), spring is connected against block (1k) outer side surface with guide slide (1j) inner wall sealing, and described first spring (1i) the other end and spring lean against block (1k) end face; Described oil-feed valve body (1a) is connected with the adjusting bolt (1m) leant against block (1k) other end with spring.
4. the oiling valve block according to claim 1 or 2 or 3, it is characterized in that, described throttle valve (1b) comprises the throttling valve core (1b1) with throttle orifice, oil-feed valve body (1a) has the first sealing lip, outside the throttle orifice of throttling valve core (1b1), there is the second sealing lip; The second spring (1b2) is provided with between described throttling valve core (1b1) and oil-feed valve body (1a), second spring (1b2) one end and throttling valve core (1b1) lean, and the other end and oil-feed valve body (1a) lean.
5. oiling valve block according to claim 4, is characterized in that, described oil-feed valve body (1a) has handling hole, and described handling hole is provided with bolt plug (1n).
6. a complex controll flow multi-way valve, is characterized in that, comprises at least two pieces of operating valve blocks (2), scavenger valve block (3) and the oiling valve block (1) as described in claim 1-5; Operating valve block (2) has oil inlet passage (2a), the first oil duct (2b), the second oil duct (2c) and drainback passage (2d); Also there is in operating valve block (2) the load-sensitive oil duct (2h) be connected with the second oil duct (2c); Be equipped with the selector valve core structure that can control oil inlet passage (2a) and the first oil duct (2b) connected state in operating valve block (2) and the first oil duct (2b) can be controlled and with the second oil duct (2c) connected state there is the pressure compensation valve core structure in the second load-sensitive chamber (2k); Selector valve core structure also comprises the load-sensitive chamber pressure release oil duct (2i) that the second oil duct (2c) can be made to be connected with drainback passage (2d); The oil inlet passage (2a) of all working valve block (2) is all connected with the oil outlet (1g) of oiling valve block (1); The load-sensitive oil duct (2h) of all working valve block (2) makes the load-sensitive oil duct (2h) that in all load-sensitive oil ducts (2h), oil pressure is the highest be connected with the first load-sensitive chamber (1e) by shuttle valve oil pressure comparative structure; Second load-sensitive chamber (2k) of all working valve block (2) is all connected with the first load-sensitive chamber (1e).
7. complex controll flow multi-way valve according to claim 6, it is characterized in that, described shuttle valve oil pressure comparative structure comprises one group of shuttle valve (4), shuttle valve (4) has two oil pressure ratios comparatively interface and external interface, external interface is connected with the first load-sensitive chamber (1e), and two oil pressure ratios comparatively interface are connected correspondingly with the load-sensitive oil duct (2h) of two pieces of operating valve blocks (2) respectively.
8. complex controll flow multi-way valve according to claim 6, is characterized in that, described shuttle valve oil pressure comparative structure comprises array shuttle valve (4), is provided with one group of shuttle valve (4) between adjacent two pieces of operating valve blocks (2); Shuttle valve (4) has two oil pressure ratios comparatively interface and external interface; All shuttle valves (4) are connected in series, the oil pressure ratio being positioned at the shuttle valve (4) between N operating valve block (2) and N+1 operating valve block (2) comparatively interface is connected with the external interface of the shuttle valve (4) be positioned between N+1 operating valve block (2) and N+2 operating valve block (2), and another oil pressure ratio being positioned at the shuttle valve (4) between N operating valve block (2) and N+1 operating valve block (2) comparatively interface is connected with the load-sensitive oil duct (2h) of N operating valve block (2); And the external interface being positioned at the shuttle valve (4) of one end is connected with the first load-sensitive chamber (1e); The oil pressure ratio being positioned at the shuttle valve (4) of the other end comparatively interface is connected with the load-sensitive oil duct (2h) of last operating valve block (2).
9. the complex controll flow multi-way valve according to claim 6 or 7 or 8, it is characterized in that, described selector valve core structure comprises changeover valve core (2f), changeover valve core (2f) has the oil-feed circular groove corresponding with oil inlet passage (2a) position and the first fuel-displaced circular groove corresponding with the first oil duct (2b) position, changeover valve core (2f) outer side surface also has the throttling groove (2g) between oil-feed circular groove and the first fuel-displaced circular groove; Load-sensitive chamber pressure release oil duct (2i) is positioned at changeover valve core (2f).
10. the complex controll flow multi-way valve according to claim 6 or 7 or 8, it is characterized in that, described pressure compensation valve core structure comprises pressure compensation spool (2j) and counter balance pocket, what have connection first oil duct (2b) and counter balance pocket in pressure compensation spool (2j) is communicated with oil duct (2m), is provided with the 3rd spring (2n) making pressure compensation spool (2j) have compression counter balance pocket trend all the time in described second load-sensitive chamber (2k).
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| CN201410084394.3A CN103790889B (en) | 2014-03-10 | 2014-03-10 | Oiling valve block and complex controll flow multi-way valve |
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| CN104088841B (en) * | 2014-06-26 | 2017-02-15 | 徐州徐工液压件有限公司 | Load sensitive hydraulic system and load sensitive valve thereof |
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| CN105003710B (en) * | 2015-07-23 | 2017-06-30 | 山东临工工程机械有限公司 | Positive flow and minus flow universal valve body structure and valve assembly |
| DE102015226608A1 (en) * | 2015-12-23 | 2017-06-29 | Robert Bosch Gmbh | Housing component with a hydraulic line |
| DE102015226610A1 (en) * | 2015-12-23 | 2017-06-29 | Robert Bosch Gmbh | Housing component with a hydraulic line |
| CN106050779B (en) * | 2016-07-18 | 2018-01-23 | 江苏恒立液压科技有限公司 | forklift multi-way valve |
| CN110388343A (en) * | 2018-04-18 | 2019-10-29 | 北京华德液压工业集团有限责任公司 | A kind of big flow single channel double overflow three-way pressure compensating device |
| CN109737111B (en) * | 2019-01-28 | 2024-01-02 | 日照海卓液压有限公司 | Multi-way valve with one-way or two-way hydraulic lock integrated oil supplementing function |
| CN109751291B (en) * | 2019-01-28 | 2024-01-02 | 日照海卓液压有限公司 | Multi-way valve with energy awakening system in reversing working unit |
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