CN103225633B - Hydraulic reversing valve, hydraulic reversing valve group and engineering machinery - Google Patents

Abstract

The invention discloses a hydraulic reversing valve, a hydraulic reversing valve group and engineering machinery, wherein the hydraulic reversing valve comprises a valve body and a valve rod, the valve body is provided with a plurality of internal flow passages, a valve hole communicated with the internal flow passages, and an oil inlet, an oil return port and a working oil port communicated with the corresponding internal flow passages, a flow guide groove is formed outside the valve rod, the valve rod can axially move in the valve hole to conduct or stop the corresponding internal flow passages, thereby the hydraulic reversing valve is switched among different working positions, and the working positions of the hydraulic reversing valve comprise a middle position, in which the hydraulic oil of the hydraulic reversing valve can return oil, the valve rod is internally provided with a valve rod flow passage, and when the valve rod is switched from the middle position to other working positions, the valve rod flow passage can be communicated with the oil inlet and the corresponding working oil port supplied with oil by the oil inlet, or can be communicated with the oil inlet and the oil return port. The hydraulic reversing valve bank provided by the invention is used by the hydraulic reversing valve, and the engineering machinery uses the hydraulic reversing valve bank provided by the invention.

Description

Hydraulicdirectional control valve, hydraulicdirectional control valve group and engineering machinery

Technical field

The present invention relates to the valve member field of hydraulic pressure commutation, particularly, relate to a kind of hydraulicdirectional control valve, use the hydraulicdirectional control valve group of this hydraulicdirectional control valve and use the engineering machinery of this hydraulicdirectional control valve group.

Background technique

In engineering machinery field, usually can use hydraulicdirectional control valve group, conveniently use and usually the hydraulicdirectional control valve group as main reversing valve is designed to integration composite valve part, i.e. multiple directional control valve.For hoist, in its main reversing valve, generally include the hydraulicdirectional control valve controlling luffing range of cantilever support and elevator folding and unfolding.These two selector valves are interconnected, with the folding and unfolding operation of the luffing range of cantilever support operation and elevator that complete hoist respectively, particularly, a selector valve controls arm support oil cylinder, and another then controls hoist motor, when two selector valves all do not commutate, the oil-feed fluid controlling the selector valve of arm support oil cylinder carries out oil return by the selector valve controlling hoist motor.Wherein, as single selector valve, the useful area due to each hydraulic fluid port is undergone mutation the impact that can cause executive component.Such as; in the selector valve with meta oil return function; often there will be hydrovalve from meta to the process that other working positions switch; because filler opening needs to actuator port supply pressure oil; the valid circulation area of its oil return is needed to diminish; and can sport in a flash very little at certain; this increases making the pressure of filler opening suddenly; thus can impact corresponding actuator port instantaneously at this; then the impact of executive component is caused; such as cause greater impact to arm support oil cylinder, this also can be able to have a negative impact to the service behaviour of engineering machinery.

In addition, in hydraulicdirectional control valve group, when the action simultaneously of multiple actuator, because corresponding multiple selector valve is interconnected, the actuator of rear action can cause and accelerate suddenly at first action actuating mechanism.Such as, when the selector valve controlling amplitude oil cylinder action is in transition position, an oil-feed fluid part for this selector valve can by controlling the selector valve oil return of hoist motor, another part is to amplitude oil cylinder fuel feeding, if now operate hoist motor simultaneously, when can operate due to the selector valve controlling hoist motor, the oil return of the selector valve controlling amplitude oil cylinder is partly blocked, and in the selector valve that this controls in a flash amplitude oil cylinder filler opening is strengthened suddenly to the flow of actuator port, this unexpected accelerating process can cause luffing range of cantilever support velocity jump and cause jib to rock, not only affect the operating characteristics of engineering machinery, but also easily cause unnecessary accident.

Therefore, provide a kind of at least can solve above-mentioned a kind of problem hydraulicdirectional control valve and the manipulation of hydraulicdirectional control valve group to engineering machinery there is positive effect.

Summary of the invention

An object of the present invention is to provide a kind of hydraulicdirectional control valve, this hydraulicdirectional control valve at least can be reduced in the degree of the impact produced when switching from meta to other working positions.

Another object of the present invention is to provide a kind of hydraulicdirectional control valve group, this hydraulicdirectional control valve group uses hydraulicdirectional control valve provided by the invention, and at least can be reduced in when switching from meta to other working positions, reduce the degree that the pressure jump due to filler opening place causes hydrovalve to impact.

Another object of the present invention is to provide a kind of engineering machinery, and this project machinery uses hydraulicdirectional control valve group provided by the invention.

To achieve these goals, the invention provides a kind of hydraulicdirectional control valve, comprise valve body and valve rod, described valve body is formed with many inner flow passages, be communicated with the valve opening of these many inner flow passages and the filler opening with respective inner flow passage, return opening and actuator port, the outside of described valve rod is formed with guiding gutter, and described valve rod can move axially with conducting or end corresponding described inner flow passage in described valve opening, thus described hydraulicdirectional control valve is switched between different operating position, and the working position of described hydraulicdirectional control valve comprises meta, at this meta, the hydraulic oil of described hydraulicdirectional control valve can oil return, wherein, described stem internal is formed with valve rod runner, described valve rod runner comprises the axial oilhole and radial direction oil hole that are interconnected, described axial oilhole extends along the axis of described valve rod, described radial direction oil hole is positioned at the opposite end of described axial oilhole and hydraulic fluid port corresponding to described hydraulicdirectional control valve is respectively communicated with, when switching from meta to other working positions, this valve rod runner can be communicated with described filler opening and the corresponding described actuator port by this filler opening fuel feeding, or described filler opening and described return opening can be communicated with.

Preferably, when switching from described meta to other working positions, described valve rod runner is communicated with described filler opening and corresponding described actuator port prior to described guiding gutter.

Preferably, when switching from described meta to other working position, described valve rod moves along a corresponding axial direction, now, and filler opening described in described valve rod flow passage and corresponding described actuator port; When switching from described meta to another other working position, described valve rod moves along contrary axial direction, now, described valve rod runner can be communicated with described filler opening and described return opening, and along with the movement of described valve rod, when being switched to another other working positions described, described valve rod runner can disconnect being communicated with of described filler opening and described return opening gradually.

Preferably, described hydraulicdirectional control valve is three position directional valve, described actuator port comprises the first actuator port and the second actuator port, described valve rod runner correspondingly comprises the first valve rod runner and the second valve rod runner that are respectively formed at described stem internal, described first valve rod runner is for being communicated with described filler opening and described second actuator port, and described second valve rod runner is for being communicated with described filler opening and described first actuator port.

Preferably, described valve body is also formed with the oil outlet for oil return.

Preferably, in described valve body, be formed with the second oil back chamber of being communicated with described oil outlet and the 3rd oil back chamber, the first oil suction chamber of being communicated with described filler opening and the second oil suction chamber and the first oil back chamber be communicated with described return opening and the 4th oil back chamber,

When described hydraulicdirectional control valve is positioned at meta, described first oil suction chamber is communicated with described 3rd oil back chamber with described second oil back chamber simultaneously, at described hydraulicdirectional control valve from meta to the process that other working positions switch, first described first oil suction chamber can be communicated with corresponding described first actuator port or described second actuator port by the described valve rod runner of described stem internal, and then described second oil suction chamber can be communicated with described first actuator port or described second actuator port by the described guiding gutter of described stem exterior.

Preferably, described second oil back chamber and described 3rd oil back chamber are respectively formed at the axial both sides of described first oil suction chamber, described first oil back chamber is formed in the axially outside of described second actuator port, and described 4th oil back chamber is formed in the axially outside of described first actuator port

The described guiding gutter of described stem exterior comprises the first guiding gutter, the second guiding gutter, the 3rd guiding gutter and the 4th guiding gutter arranged vertically successively,

Described first valve rod runner comprise be positioned at axially inner side first inside radial direction oil hole, be positioned at the first outer radial oilhole in axially outside and be communicated with the first axial oilhole of this radial direction oil hole and the first outer radial oilhole inside first, described second valve rod runner comprise be positioned at axially inner side second inside radial direction oil hole, be positioned at the second outer radial oilhole in axially outside and be communicated with the second axial oilhole of this second outer radial oilhole and the second outer radial oilhole

The outside of described valve rod is also formed and is positioned at the axial both sides of described first guiding gutter and the first segment chute be communicated with this first guiding gutter, and be positioned at the axial both sides of described 4th guiding gutter and the second section chute be communicated with the 4th guiding gutter, inside described first, inside radial direction oil hole and described second, radial direction oil hole lays respectively in described second guiding gutter and described 3rd guiding gutter

Described inner flow passage in described valve body comprises the first inner flow passage and the second inner flow passage that are communicated with described second oil suction chamber and described valve opening respectively, and be communicated with the 3rd inner flow passage of described first actuator port and described valve opening and the 4th inner flow passage being communicated with described second actuator port and described valve opening

When described meta, described first outer radial oilhole and described second outer radial oilhole are the first length with the axial distance of described first oil back chamber and described 4th oil back chamber respectively, be the second length with the axial distance of described 3rd runner and described 4th runner respectively, the inner side cut-off end of described second guiding gutter and described 3rd guiding gutter is the 3rd length with the axial distance at the edge of described first oil suction chamber respectively, the inner of the inner and described second section chute of described first segment chute is the 4th length with the axial distance of described first inner flow passage and the second inner flow passage respectively, described first guiding gutter and described 4th guiding gutter are the 5th length with the axial distance of described first inner flow passage and the second inner flow passage respectively,

Wherein, described first length, described second length, described 3rd length, described 4th length and described 5th length become large successively.

Preferably, when described meta, cut-off end in the outside of described second guiding gutter and described 3rd guiding gutter is the 6th length with the axial distance at described second oil back chamber and described 3rd oil back chamber edge respectively, and described 6th length is greater than described 5th length.

According to a further aspect in the invention, provide a kind of hydraulicdirectional control valve group, comprise multiple interconnective selector valve, its wherein, one of them described selector valve is hydraulicdirectional control valve provided by the invention.

Preferably, described multiple selector valve comprises the first selector valve and the second selector valve, described first selector valve is described hydraulicdirectional control valve, described second selector valve is three six-way transfer valves, the described oil outlet of described first selector valve is communicated with described second selector valve, and when described second selector valve is positioned at meta, described oil outlet is by described second selector valve oil return, when other working positions, described oil outlet is ended by described second selector valve.

In accordance with a further aspect of the present invention, provide a kind of engineering machinery, this project machinery comprises multiple actuator and controls the main reversing valve of the plurality of actuator action, and wherein, described main reversing valve is claim hydraulicdirectional control valve group provided by the invention.

Preferably, described engineering machinery is hoist, this hoist comprises amplitude oil cylinder, hoist motor and controls the described main reversing valve of this amplitude oil cylinder and hoist motor action, described main reversing valve comprises the first selector valve controlling described amplitude oil cylinder, and control the second selector valve of described hoist motor, and be provided with the second one-way valve between described first selector valve and described second selector valve, this second one-way valve allows fluid to flow to described second selector valve from described first selector valve.

Preferably, described first selector valve is described hydraulicdirectional control valve, described second selector valve is three six-way transfer valves, the described oil outlet of described first selector valve is communicated with described second selector valve, when described second selector valve is positioned at meta, described oil outlet is by described second selector valve oil return, and when other working positions, described oil outlet is ended by described second selector valve.

Pass through technique scheme, stem internal due to hydraulicdirectional control valve provided by the invention is formed with valve rod runner, when switching from meta to other working positions, in the pressure jump at filler opening place, due to the existence of valve rod runner, when valve rod flow passage filler opening and actuator port, the pressure of filler opening and actuator port can keep equal substantially, and when valve rod flow passage filler opening and return opening, unnecessary fluid can be made to return opening oil return, therefore the pressure of relevant work hydraulic fluid port can not be made to increase suddenly, namely due to the buffer function of valve rod runner, only the pressure of actuator port can be made to raise gradually, thus reduce the degree occurring to impact.In addition, because the valve rod runner that the invention provides the hydraulicdirectional control valve in hydraulicdirectional control valve group can also be communicated with filler opening and return opening, therefore, it is possible to ensure that the flow of actuator port remains unchanged substantially, therefore, it is possible at least reduce the degree that velocity jump occurs, therefore, the practicability of hydraulicdirectional control valve provided by the invention, hydraulicdirectional control valve group and engineering machinery is made to strengthen.

Other features and advantages of the present invention are described in detail in embodiment part subsequently.

Accompanying drawing explanation

Accompanying drawing is used to provide a further understanding of the present invention, and forms a part for specification, is used from explanation the present invention, but is not construed as limiting the invention with embodiment one below.In the accompanying drawings:

Fig. 1 is the hydraulic schematic diagram of the hydraulicdirectional control valve group in preferred implementation provided by the invention;

Fig. 2 is the sectional structure schematic diagram (valve rod does not cut open) of the hydraulicdirectional control valve in preferred implementation provided by the invention;

Fig. 3 is the sectional structure schematic diagram intercepted from the line A-A Fig. 2.

Description of reference numerals

1 valve body 2 valve rod

3 first one-way valve 4 first selector valves

5 second selector valve 6 main reversing valves

7 second one-way valves

11 inner flow passage 12 valve openings

21 guiding gutter 22 valve rod runners

23 first segment chute 24 second section chutes

111 first inner flow passage 112 second inner flow passages

113 the 3rd inner flow passage 114 the 4th inner flow passages

211 first guiding gutter 212 second guiding gutters

213 the 3rd guiding gutter 214 the 4th guiding gutters

221 axial oilhole 222 radial direction oil hole

22a first valve rod runner 22b second valve rod runner

P, P ' filler opening T return opening

A first actuator port B second actuator port

C the 3rd actuator port D the 4th actuator port

AB actuator port T1 first oil back chamber

T2 second oil back chamber T3 the 3rd oil back chamber

T4 the 4th oil back chamber

Radial direction oil hole 22ab first outer radial oilhole inside 22aa first

Radial direction oil hole 22bb second outer radial oilhole inside 22ba second

A, b, c, d, e, f, g first, second, third, fourth, the 5th, the 6th, the 7th length

Embodiment

Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.Should be understood that, embodiment described herein, only for instruction and explanation of the present invention, is not limited to the present invention.

In the present invention, when not doing contrary explanation, the noun of locality used such as " upper and lower " is for benchmark defines with the page of accompanying drawing 2 and Fig. 3, " inside and outside " is then for benchmark with the axial centre of valve rod, corresponding part is inner side close to the side of this axial centre, and be outside away from the side of this axial centre, in addition, " axial and radial " defines based on the length direction of valve rod, namely the length direction of valve rod is axial direction, and radial direction is perpendicular to this length direction.It should be noted that, these nouns of locality, only for illustration of the present invention, are not limited to the present invention.

It should be noted that in addition; hydraulic schematic diagram as shown in Figure 1 just indicates the working principle of hydraulicdirectional control valve group provided by the invention; the hydraulicdirectional control valve group that can realize above-mentioned working principle to those skilled in the art can be designed as the multiple directional control valve of integration composite valve form; the form connected by single valve member by pipeline can also be designed to, all should drop in protection scope of the present invention for this mode of texturing.

In addition, hydraulicdirectional control valve provided by the invention for convenience of description, be described at the main reversing valve 6 of the hoist of this hydraulicdirectional control valve that main connected applications preferred embodiment for the present invention is provided, in other embodiments, can also hydraulicdirectional control valve provided by the invention be applied in the manipulation of Other Engineering machinery, this present invention is not limited.Wherein, as shown in Figure 1, this main reversing valve 6 at least comprise that the preferred embodiment for the present invention provides for controlling the first selector valve 4 of luffing range of cantilever support operation and the second selector valve 5 for controlling elevator folding and unfolding operation, wherein two selector valves all preferably can three six-way transfer valves of meta oil return, therefore, the shock problem described in two hydraulicdirectional control valves background technique all of the present invention do not improved, especially on two transition positions (positions between meta and two working positions) of the first selector valve 4.In addition, if the first selector valve 4 and the second selector valve 5 do not improve, then while operation first selector valve 4, operate the second selector valve 5 again, because the meta oil return valid circulation area of the first selector valve 4 can diminish, and can undergo mutation instantaneously at certain, the actuator port flow of the first selector valve 4 can be made like this to increase suddenly, thus cause the speed of the amplitude oil cylinder controlling luffing range of cantilever support to increase suddenly, and cause the unstability of crane job.

In order to solve the above problems, first the present invention provides a kind of hydraulicdirectional control valve of improvement, as shown in Figures 2 and 3, this pilot operated directional control valve comprises valve body 1 and valve rod 2, oil inlet P, oil return inlet T and actuator port AB that valve body 1 is formed with many inner flow passages 11, is communicated with the valve opening 12 of these many inner flow passages 11 and is communicated with respective inner runner 11, wherein those skilled in the art can know Placement and the working principle of each hydraulic fluid port of hydraulicdirectional control valve.Wherein, the quantity of actuator port AB is set to two usually, to pass through one of them actuator port to actuator's fuel feeding, and the oil return of actuator is completed by another actuator port, such as in a preferred embodiment of the invention, in order to control the luffing of arm support oil cylinder, the first actuator port A and the second actuator port B of hydraulicdirectional control valve can be connected rod chamber and the rodless cavity of amplitude oil cylinder respectively, thus complete corresponding luffing operation.In addition, the implication of the oil inlet P of selector valve is the hydraulic fluid port that this selector valve is directly or indirectly communicated with oil hydraulic pump equal pressure oil sources, to obtain working pressure oil, the hydraulic fluid port that the implication of oil outlet T is then directly or indirectly communicated with oil sump tank for this selector valve, not drive actuator, and realize the off-load of respective execution mechanisms.And in hydraulicdirectional control valve provided by the invention, the outside of valve rod 2 is formed with guiding gutter 21, and valve rod 2 can move axially with conducting or end corresponding each inner flow passage 11 in valve opening 12, particularly, hydraulicdirectional control valve provided by the invention is spool-type valves, valve rod 2 outside is formed with guiding gutter 21, this guiding gutter 21 comprises groove part and forms this groove part and be positioned at the convex shoulder of its relative both sides, therefore the corresponding inner flow passage 11 of groove part conducting can be passed through, and end corresponding inner flow passage 11 by convex shoulder, thus oil inlet P can be communicated with from different actuator port AB with oil return inlet T.Thus realize hydraulicdirectional control valve between different operating position switch by completing the states such as the circulation of hydraulic pressure wet goods fluid in valve body, cut-off or commutation, such as realize stretching out or the operating mode such as retraction of amplitude oil cylinder.For the working principle of above-mentioned hydraulicdirectional control valve, one of ordinary skill in the art will readily recognize that not do at this and too much repeat.

Wherein, the working position of hydraulicdirectional control valve provided by the invention comprises meta, at this meta, the hydraulic oil of hydraulicdirectional control valve can oil return, this oil return can be by the direct oil return of meta drainback passage from oil inlet P, to make actuator not work, also can be from actuator port AB oil return, to make the off-load of corresponding actuator.Therefore in order to solve the shock problem owing to occurring when switching from meta to other working positions provided in background technique, in hydraulicdirectional control valve provided by the invention, valve rod 2 inside is formed with valve rod runner 22, and when switching from meta to other working positions, this valve rod runner 22 at least can be communicated with oil inlet P and the relevant work hydraulic fluid port AB by this oil inlet P fuel feeding.Therefore, due to the existence of valve rod runner 22, under certain conditions oil inlet P can be communicated with corresponding actuator port AB, thus make the pressure of oil inlet P and actuator port AB can substantially keep equal, even if therefore when oil inlet P becomes large suddenly by the valid circulation area that guiding gutter 21 and inner flow passage 11 enter relevant work hydraulic fluid port AB, also the situation that the pressure of oil inlet P to relevant work hydraulic fluid port AB increases suddenly can not be there is, namely, due to the buffer function of valve rod runner 22, only the pressure of corresponding actuator port AB can be made to raise gradually, thus the degree occurring to impact can be at least reduced, and the practicability of hydraulicdirectional control valve group provided by the invention and engineering machinery is strengthened.It should be noted that, valve rod runner 22 is when this hydraulicdirectional control valve is in meta, and the hydraulic oil in this valve rod is in the state of blocking, and namely now the pressure oil at filler opening place can not be communicated to actuator port AB through valve rod runner 22.

Wherein, preferably, when this hydraulicdirectional control valve switches from meta to other working positions, when namely hydraulicdirectional control valve is in transition position, valve rod runner 22 is communicated with oil inlet P and corresponding actuator port AB prior to inner flow passage 11 with guiding gutter 21.The buffer function of valve rod runner 22 can be made so more obvious, avoid when the guiding gutter 21 by valve rod 2 outside is directly communicated with oil inlet P and corresponding actuator port AB with inner flow passage 11, to the greater impact of actuator port AB.

In addition optionally, in some cases, this hydraulicdirectional control valve can also be communicated with oil inlet P and oil return inlet T by valve rod runner 22, even if the valid circulation area sudden change of therefore meta oil return is to very little, unnecessary fluid also can by valve rod runner 22 to oil return inlet T oil return, also the situation that the pressure of oil inlet P to relevant work hydraulic fluid port AB increases suddenly can not be there is, namely, due to the buffer function of valve rod runner 22, only the pressure of corresponding actuator port AB can be made to raise gradually, thus the degree occurring to impact can be at least reduced, and the practicability of hydraulicdirectional control valve group provided by the invention and engineering machinery is strengthened.

Wherein, in a preferred embodiment of the invention, the effect of optimization and poppet stem runner 22 more, preferably, when hydraulicdirectional control valve switches from meta to other working position, valve rod 2 moves along a corresponding axial direction, and now, valve rod runner 22 is communicated with oil inlet P and corresponding actuator port AB; And when switching from meta to another other working position, valve rod 2 moves along contrary axial direction, and now, this valve rod runner 22 can be communicated with oil inlet P and oil return inlet T, and along with the movement of valve rod 2, this valve rod runner 22 can also disconnect being communicated with of oil inlet P and oil return inlet T gradually.Namely, there is to realize a lot of selector valve the situation of multiple working position, need to make the valve rod runner 22 being opened in valve rod 2 inside itself have two effects, first when valve rod 2 moves facing one direction, hydraulicdirectional control valve can be made to enter the state of a certain working position, this valve rod runner 22 can complete above-mentioned connection oil inlet P and the effect of actuator port AB, and when valve rod 2 moves towards another direction, when hydraulicdirectional control valve can be made to enter another working position, along with the movement of valve rod 2, same valve rod runner 22 can also play another effect by connection oil inlet P and oil return inlet T: oil inlet P namely can be assisted to carry out oil return by meta drainback passage, the fluid making oil inlet P place unnecessary can by valve rod runner 22 to oil return inlet T oil return, thus ensure when the valid circulation area of meta drainback passage diminishes suddenly further, the unnecessary pressure oil of oil inlet P is by this valve rod runner 22 oil return, the pressure making oil inlet P flow to the fluid of actuator port AB can not be undergone mutation, and due to the movement along with valve rod 2, switch completely at this another working position, this valve rod runner 22 can also disconnect oil inlet P and oil return inlet T gradually, therefore the normal work of another working position can not be hindered.

It will be appreciated that, when hydraulicdirectional control valve switches from meta to a corresponding working position, oil inlet P is that throttling is communicated with by valve rod runner 22 with being communicated with of relevant work hydraulic fluid port AB, and throttling action is more and more less, and when being switching to another work corresponding, oil inlet P is communicated with also for throttling is communicated with by valve rod runner 22 and oil return inlet T, but its throttling action is increasing, it is final when valve rod moves into place, block the running of hydraulic power oil between oil inlet P and oil return inlet T, therefore just finally can realize the normal work of relevant work position.Therefore, also there is the function of auxiliary oil return by arranging valve rod runner 22, can, while the overall structure of valve member is optimized, the performance of valve body be optimized further.

And more preferably, in three position directional valve, the advantage of this design is the most outstanding.Namely in a preferred embodiment of the invention, preferably, in this three position directional valve, actuator port AB comprises the first actuator port A and the second actuator port B, valve rod runner 22 correspondingly comprises the first valve rod runner 22a and the second valve rod runner 22b that are respectively formed at valve rod 2 inside, first valve rod runner 22a is communicated with oil inlet P and the second actuator port B, second valve rod runner 22b is communicated with oil inlet P and the first actuator port A, particularly, this first valve rod runner 22a and the second valve rod runner 22b lays respectively at the both sides of valve rod 2 axial centre.Because this three position directional valve is when switching from meta to different operating position, the movement direction of valve rod 22 is contrary, therefore by above-mentioned two valve rod runners 22, no matter switch from meta to which working position, wherein namely a valve rod runner 22 can play the effect being communicated with oil inlet P and relevant work hydraulic fluid port AB, and another valve rod runner 22 then can play the effect being communicated with oil inlet P and oil return inlet T.Thus realize above-mentioned object of the present invention in an optimal manner.

Get back on this body structure of valve rod runner 22 provided by the invention, wherein as shown in Figure 3, in preferred implementation provided by the invention, valve rod runner 22 comprises the axial oilhole 221 and radial direction oil hole 222 that are interconnected, axial oilhole 221 extends along the axis of valve rod 2, and radial direction oil hole 222 is positioned at the opposite end of described axial oilhole 221 and hydraulic fluid port corresponding to described hydraulicdirectional control valve is respectively communicated with.Particularly, can be communicated with corresponding oil inlet P, corresponding actuator port AB or corresponding oil return inlet T.That is, realize oil inlet P and corresponding actuator port AB by the radial direction oil hole 222 of the axial oilhole 221 and these axial oilhole 221 two ends that are opened in stem internal, and realize being communicated with of oil inlet P and oil return inlet T.Particularly, such as conveniently process the first valve rod runner 22a in the preferred embodiment for the present invention and the second valve rod runner 22b, can hole at the two ends of valve rod 2 to offer two axial oilholes 221 do not communicated first respectively, then the sidewall of valve rod 2 hole respectively to offer corresponding radial direction oil hole 222 thus connection shaft to oilhole 221, in real work, the open end of axial oilhole 221 can use the shutoff such as plug, thus completes the corresponding function of above-mentioned valve rod runner 22.Wherein, for those skilled in the art of the present invention, in other embodiments, valve rod runner 22 also has more shape changeable, and these distortion all should drop in protection scope of the present invention.

Introduced the valve rod runner 22 in hydraulicdirectional control valve provided by the invention structure and prevent impact functional structure after, introduce valve rod runner 22 below in conjunction with hydraulicdirectional control valve group provided by the invention and how to solve the acceleration problem described in background technique.

Wherein, in engineering machinery provided by the invention, main reversing valve 6 is usually used to carry out the manipulation of various executive component.This main reversing valve 6 is hydraulicdirectional control valve group provided by the invention, this hydraulicdirectional control valve group comprises interconnective multiple selector valve, and wherein, at least one selector valve is hydraulicdirectional control valve provided by the invention, and first it should be noted that, in order to coordinate the use of this hydraulicdirectional control valve group, in hydraulicdirectional control valve provided by the invention, valve body 1 is also formed with the oil outlet P3 as meta drainback passage, and be connected with another selector valve by this oil outlet P3, and by preferably, oil return can be realized by the meta of another selector valve.Particularly, as shown in Figure 1, multiple selector valve comprises the first selector valve 4 and the second selector valve 5, first selector valve 4 is hydraulicdirectional control valve provided by the invention, second selector valve 5 is three six-way transfer valves, the oil outlet P3 of the first selector valve is communicated with the second selector valve 5, when the first selector valve 4 and the second selector valve 5 are positioned at meta, oil outlet P3 is by the second selector valve 5 oil return, when other working positions, because the second selector valve 5 needs to carry out different work, therefore oil outlet P3 is then ended by the second selector valve 5.The working principle of this second selector valve 5 and the working principle of the first selector valve 4 similar, it is mainly through oil inlet P ', return opening (do not mark, in integrated form combination valve multiple directional control valve, the oil return inlet T of this return opening and the first selector valve is the oil return inlet T of main reversing valve 6) and the first actuator port C and the second actuator port D realize to actuator's such as hoist motor control.And preferably, in the control of hoist of the present invention, the second one-way valve 7 is provided with between first selector valve 4 and the second selector valve 5, this second one-way valve 7 allows fluid to flow to the second selector valve 5 from the first selector valve 4, so that the control of the hoist motor of amplitude oil cylinder can be completed, and the interflow fuel feeding of double pump to hoist motor can be realized by two selector valves.

Can find out in composition graphs 1 and Fig. 3, when the first selector valve 4 is in transition position, namely both some passed through valve rod runner 22 to actuator port AB fuel feeding to the fluid of the oil inlet P of the first selector valve 4, some carries out oil return by oil outlet P3 from the second selector valve 5 again, if now operate the second selector valve 5 simultaneously, first selector valve 4 is truncated by the oil return part of the second selector valve 5, unnecessary fluid has the trend flowing to actuator port AB from oil inlet P, if the first selector valve 4 does not improve, the corresponding actuator port AB being fed to the first selector valve 4 at the more heavy wool liquid of the first selector valve 4 switched from meta to other working positions can be made, namely the hydraulic fluid flow rate of actuator port is increased, the actuator that the first selector valve 4 then can be caused to control such as arm support oil cylinder speed increases, even also also can suddenly change by flow in a flash at certain.Such as while the operation carrying out luffing range of cantilever support, when not having improvement first selector valve 4 to be in transition position, when operating elevator folding and unfolding again, arm support oil cylinder can be made to occur to accelerate suddenly by the first selector valve 4, there is comparatively serious safety problem by causing hoist in this unexpected acceleration.

And owing to employing hydraulicdirectional control valve provided by the invention, because oil inlet P and oil return inlet T also can be communicated with (as in Fig. 1, in the figure drawings of the first selector valve 4, the connection in-line added is the same with the schematic channel of oil circuit), under the connection effect of valve rod runner 22, unnecessary fluid can be made to flow back to oil return inlet T from valve rod runner 22, thus the flow of actuator port AB can not be made to change, the degree that actuator port AB flow increases is reduced to I haven't seen you for ages, thus avoid the velocity jump of actuator's such as arm support oil cylinder, ensure that the Security of the engineering machinery such as hoist.Make the performance of hydraulicdirectional control valve group provided by the invention higher.

Above-mentioned two important function mainly describing valve rod runner 22 in hydraulicdirectional control valve provided by the invention, are described in detail the structure of hydraulicdirectional control valve provided by the invention and working procedure below in conjunction with accompanying drawing 2 and Fig. 3.

First structurally, in order to realize above-mentioned hydraulicdirectional control valve and hydraulicdirectional control valve group, in a preferred embodiment of the invention, the the second oil back chamber T2 and the 3rd oil back chamber T3 that are communicated with oil outlet P3 is formed in valve body 1, the the first oil suction chamber P1 be communicated with oil inlet P and the second oil suction chamber P2, and the first oil back chamber T1 to be communicated with oil return inlet T and the 4th oil back chamber T4, wherein the second oil back chamber T2 and the 3rd oil back chamber T3 is communicated by oil outlet P3, namely hydraulicdirectional control valve is three six-way transfer valves, and between meta and two working positions, also there is corresponding transitional operation position.Wherein, when hydraulicdirectional control valve is positioned at meta, second oil back chamber T2 of the first oil suction chamber P1 both sides relative to laying respectively at it is communicated with the 3rd oil back chamber T3 simultaneously, namely realize realizing oil return by the meta of oil outlet P3, the second one-way valve 7 and the second selector valve 5, and described second oil back chamber T2 and the 3rd oil back chamber T3 are communicated with the radial direction oil hole 222 of the inner side of two articles of valve rod runners 22 respectively when meta.At hydraulicdirectional control valve from meta to the process that other working positions switch, first the first oil suction chamber P1 can be communicated with the first corresponding actuator port A or the second actuator port B by the valve rod runner 22 of valve rod 2 inside, and then the second oil suction chamber P2 can be communicated with the first actuator port A or the second actuator port B with guiding gutter 21 by the inner flow passage 11 of valve rod 2 outside.Wherein be provided with the first one-way valve 3 between the second oil suction chamber P2 and actuator port AB, need first to build the pressure before being communicated with actuator port AB by guiding gutter 21 to make the second oil suction chamber P2, after equal pressure reaches the cracking pressure of the first one-way valve 3, the first one-way valve 3 can be opened, pass through guiding gutter 21 again to actuator port AB fuel feeding, provide the stability of hydraulicdirectional control valve work.

More specifically, as shown in Figures 2 and 3, second oil back chamber T2 and the 3rd oil back chamber T3 is respectively formed at the axial both sides of the first oil suction chamber P1, first oil back chamber T1 is formed in the axially outside of the second actuator port B, 4th oil back chamber T4 is formed in the axially outside of the first actuator port A, the guiding gutter 21 of stem exterior comprises the first guiding gutter 211 arranged vertically successively, second guiding gutter 212, 3rd guiding gutter 213 and the 4th guiding gutter 214, wherein, described first guiding gutter 211 is for being communicated with described second actuator port B, 4th guiding gutter 214 is for being communicated with described first actuator port A, second guiding gutter 212 to be arranged between the first oil suction chamber P1 with the second oil back chamber T2 and for being communicated with the first oil suction chamber P1 and the second oil back chamber T2, 3rd guiding gutter 213 to be arranged between the first oil suction chamber P1 with the 3rd oil back chamber T3 and for being communicated with the first oil suction chamber P1 and the 3rd oil back chamber T3, valve rod 2 between described second guiding gutter 212 and the 3rd guiding gutter 213 is provided with convex shoulder, and this convex shoulder is positioned at described first oil suction chamber P1.First valve rod runner 22a comprise be positioned at axially inner side first inside radial direction oil hole 22aa, be positioned at the first outer radial oilhole 22ab in axially outside and be communicated with the first axial oilhole 221a of this radial direction oil hole 22aa and the first outer radial oilhole 22ab inside first, second valve rod runner 22b comprise be positioned at axially inner side second inside radial direction oil hole 22ba, be positioned at the second outer radial oilhole 22bb in axially outside and be communicated with the second axial oilhole 221b of this second outer radial oilhole 22ba and the second outer radial oilhole 22bb, thus can not only complete the first oil suction chamber P1 and the second actuator port B by the first valve rod runner 22a and the second valve rod runner 22b, the connection of the first actuator port A, being communicated with of the first oil suction chamber P1 and the first oil back chamber T1 and the 4th oil back chamber T4 can also be completed.

In addition, in order to realize the oil return of actuator port AB when meta, also preferably, the outside of valve rod 2 is also formed and is positioned at the first axial both sides of guiding gutter 211 and the first segment chute 23 be communicated with this first guiding gutter 211, and be positioned at the 4th axial both sides of guiding gutter 214 and the second section chute 24 be communicated with the 4th guiding gutter 214, namely can be communicated with the second actuator port B and the first oil back chamber T1 by this first segment chute 23, the first actuator port A and the 4th oil back chamber T4 can be communicated with by second section chute 24.In addition, inside first, inside radial direction oil hole 22aa and second, radial direction oil hole 22ba lays respectively in the second guiding gutter 212 and the 3rd guiding gutter 213, therefore, when meta, the first valve rod runner 22a all can be communicated with the first oil suction chamber P1 with the inner side of the second valve rod runner 22b.In addition, inner flow passage 11 in valve body 1 comprises the first inner flow passage 111 and the second inner flow passage 112 being communicated with the second oil suction chamber P2 and valve opening 12 respectively, and is communicated with the 3rd inner flow passage 113 of the second actuator port B and valve opening 12 and the 4th inner flow passage 114 etc. being communicated with the first actuator port A and valve opening 12.

When meta, first outer radial oilhole 22ab and the second outer radial oilhole 22bb is the first length a with the axial distance of the first oil back chamber T1 and the 4th oil back chamber T4 respectively, be the second length b with the axial distance of the 3rd runner 113 and the 4th runner 114 respectively, wherein in order to meet above-mentioned first length a and the second length b simultaneously, two length are completed by different outer radial oilholes respectively, such as each valve rod runner 22 all shows two outer radial oilholes in fig. 2, these two outer radial oilholes can meet above-mentioned first length a and the second length b respectively, certainly in some embodiments, also can design an outer radial oilhole and meet the first length a and the second length b simultaneously, this type of distortion is dropped in protection scope of the present invention equally, in addition herein or following in mentioned " axial distance " that relate to oilhole be this oilhole and other chambeies, runner, the parts such as the throttling groove minimum axial direction distance that can be communicated with each other, the such as axial distance of above-mentioned first outer radial oilhole and the first oil back chamber T1, for the minimum axial direction distance that the two is communicated with can be realized, the i.e. axial distance at the edge of oilhole and the edge of oil back chamber.

Due to when meta, the radial direction oil hole 222 of the inner side of two valve rod runners 22 is all communicated with the first oil suction chamber P1, therefore after valve rod 2 moves the first length a from meta, corresponding valve rod runner 22 can be made to be communicated with oil inlet P and oil return inlet T by the radial hydraulic fluid port 222 in outside, after further moving to the second length b, then can be communicated with oil inlet P and corresponding actuator port AB.Also the outer end of preferred first segment chute 23 and second section chute 24 is also the second length b with the axial distance of the first oil back chamber T1 and the 4th oil back chamber T4 respectively in addition, therefore, after valve rod 2 moves the second length b, can disconnect between corresponding actuator port AB and adjacent oil back chamber and being communicated with.

In addition, inner side cut-off end (the corresponding side of the convex shoulder namely between the second guiding gutter 212 and the 3rd guiding gutter 213) of the second guiding gutter 212 and the 3rd guiding gutter 213 is the 3rd length c with the axial distance at the edge of the first corresponding oil suction chamber P1 respectively, therefore, after valve rod 2 moves and reaches the 3rd length c, the circulation area of the second guiding gutter 212 and the first oil suction chamber P1 will diminish suddenly, and the second oil back chamber T2 is disconnected with the first oil suction chamber P1 be communicated with, or the circulation area of the 3rd guiding gutter 213 and the first oil suction chamber P1 diminishes, and the 3rd oil back chamber T3 and the first oil suction chamber P1 is disconnected.In addition, the inner of the inner and second section chute 24 of first segment chute 23 is the 4th length d with the axial distance of the first inner flow passage 111 and the second inner flow passage 112 respectively, namely, when valve rod displacement distance reaches the 4th length d, the second oil suction chamber P2 will be begun through to corresponding actuator port AB fuel feeding; And the first guiding gutter 211 and the 4th guiding gutter 214 are the 5th length e with the axial distance of the first inner flow passage 111 and the second inner flow passage 112 respectively, therefore, after valve rod moves to the 5th length e, the flow from the second oil suction chamber P2 to corresponding actuator port AB fuel feeding will increase further gradually.And as important design, wherein, the first length a, the second length b, the 3rd length c, the 4th length d and the 5th length e become large successively, and namely this above-mentioned process will occur successively.Therefore summarily, move down for valve rod 22, after the distance of valve rod 22 movement is greater than a, the second valve rod runner 22b can be communicated with the first oil suction chamber P1 and the 4th oil back chamber T4; After the distance of valve rod 22 movement is greater than b, the first valve rod runner 22a can be communicated with the first oil suction chamber P1 and the first actuator port B; After displacement distance is greater than c, the oil return of oil outlet P3 significantly reduces; After being greater than d, the second oil suction chamber P2 can start to the second actuator port B fuel feeding, and therefore in the process of a to e, hydraulicdirectional control valve provided by the invention and hydraulicdirectional control valve group effectively can prevent the phenomenon of impacting and accelerating.

In addition, also preferably, when meta, cut-off end in the outside of the second guiding gutter 212 and the 3rd guiding gutter 213 is the 6th length f with the axial distance at the second oil back chamber T2 and the 3rd oil back chamber T3 edge respectively, and the 6th length f is greater than the 5th length e.After valve rod 2 displacement distance is greater than e, flow from the second oil suction chamber P2 to the second actuator port B2 increases gradually, until after displacement distance is greater than f, then hydraulicdirectional control valve passes through the first guiding gutter 211 to the second actuator port B2 fuel feeding by the second fuel supply chamber P2 completely, second valve rod runner 22b is then cut off, and disconnects being communicated with of the first oil suction chamber P1 and the 4th oil back chamber T4.That is, hydraulicdirectional control valve reaches the final function of relevant work position, in addition, as the g in Fig. 2 represents seven length of valve rod 2 to spring seat, is also the range that valve rod 2 one working positions switch.

Axially will move down with valve rod 2 below, the process of hydraulicdirectional control valve when upwards position switches from meta introduces the working procedure of hydraulicdirectional control valve provided by the invention and hydraulicdirectional control valve group in detail.

1) when the first selector valve 4 is failure to actuate, when only the second selector valve 5 being operated, when the inlet pressure of the second selector valve 5 is less than the return pressure of the first selector valve 4 after oil outlet P3, oil inlet P, P ' interflow is the second selector valve 5 fuel feeding, when the inlet pressure of the second selector valve 5 is greater than the return pressure of the first selector valve 4 after oil outlet P3, blocked the oil return at the oil outlet P3 mouth place of the first selector valve 4 by the second one-way valve 7;

2) when the first selector valve 4 valve rod 2 relative to valve body 1 move down distance be greater than a be less than b time, first oil suction chamber P1 and the second oil back chamber T2 chamber are in throttling communicating state, also throttling communicating state is gradually become with the 3rd oil back chamber T3, 3rd oil back chamber T3 enters the second axial oilhole 221b by radial direction oil hole 22ba inside second, communicate with the 4th oil back chamber T4 through the second outer radial oilhole 22bb again, second actuator port B is communicated with the first oil back chamber T1 throttling by the 3rd throttling groove 23, under this state, the second actuator port B of the first selector valve 4 is not owing to having pressure oil supply, to not work, if link manipulation second selector valve 5 under this state, the part fluid that first oil suction chamber P1 carries out oil return by oil outlet P3 is blocked, unnecessary fluid will enter the second axial oilhole 221b by radial direction oil hole 22ba inside second, the 4th oil back chamber T4 is entered again through the second outer radial oilhole 22bb, thus flow back to oil return inlet T, because now the second actuator port B communicates with the first oil back chamber T1 throttling, fluid will enter oil return inlet T further, if when the induced pressure of the second selector valve 5 is lower, first oil suction chamber P1 also can some fluid by the second one-way valve 7 and oil inlet P ' fluid that provides collaborates to think the second selector valve 5 fuel feeding,

3) when the first selector valve 4 valve rod 2 relative to valve body 1 move down distance be greater than b be less than c time, first oil suction chamber P1 and the second oil back chamber T2 is in stronger throttling communicating state, also stronger throttle will be in the 3rd oil back chamber T3, and the increase with valve rod 2 displacement is strengthened by throttle, second actuator port B was truncated with the first being communicated with of oil back chamber T1, fluid enters the first axial oilhole 221a by radial direction oil hole 22aa inside first, and enter actuator port B by the first outer radial oilhole 22ab, amplitude oil cylinder work can be promoted after oil pressure reaches certain value, if link manipulation second selector valve 5 in this case, first oil suction chamber P1 will enter the second axial oilhole 221b by radial direction oil hole 22ba inside second by the fluid entering the 3rd oil back chamber T3, the 4th oil back chamber T4 is entered again through the second outer radial oilhole 22bb, thus flow back to oil return inlet T.If when the induced pressure of the second selector valve 5 is low, also can some fluid by the second one-way valve 7 and oil inlet P ' fluid that provides collaborates to be the second selector valve 5 fuel feeding, in a word, link manipulation second selector valve 5 in this case, enter from radial direction oil hole 22aa inside first speed that first axial oilhole 221a enters the fluid of the second actuator port B by the first outer radial oilhole 22ab again by the first oil suction chamber P1 substantially constant, therefore do not affect luffing action;

4) when the valve rod 2 of the first selector valve 4 moves down apart from when just will reach c relative to valve body 1, effective flow area that first oil suction chamber P1 enters the 3rd oil back chamber T3 by restriction will reduce suddenly, the pressure of the first oil suction chamber P1 will increase suddenly, but due to the buffer function of the first valve rod runner 22a, first oil suction chamber P1 enters the oil pressure of the second actuator port B by radial direction oil hole 22aa, the first axial oilhole 221a inside first, the first outer radial oilhole 22ab will increase gradually, thus can not produce too large impact at the second actuator port B;

5) when the first selector valve 4 valve rod 2 relative to valve body 1 move down distance be greater than c be less than d time, first oil suction chamber P1 and the second oil back chamber T2 is in stronger throttling communicating state, increase with valve rod 2 displacement is strengthened by throttle, first oil suction chamber P1 is in direct connection of the 3rd oil back chamber T3 the state of blocking, a fluid part of first oil suction chamber P1 is entered the first axial oilhole 221a by radial direction oil hole 22aa inside first and is entered the second actuator port B by the first outer radial oilhole 22ab, amplitude oil cylinder work can be promoted after oil pressure reaches certain value, another part can enter the second oil back chamber T2 by the restriction between the first oil suction chamber P1 and the second oil back chamber T2, as shown in Figure 3, because the second oil back chamber T2 and the 3rd oil back chamber T3 is in communicating state with oil outlet P3 all the time, if link manipulation second selector valve 5 in this case, first oil suction chamber P1 will enter the second axial oilhole 221b by radial direction oil hole 22ba inside second by the restriction of the second oil back chamber T2 to the part fluid of the 3rd oil back chamber T3, oil return inlet T is entered again through the second outer radial oilhole 22bb, if the induced pressure of the second selector valve 5 is when comparatively oil outlet P3 is low, also can some fluid by the second one-way valve 7 and oil inlet P ' fluid that provides collaborates to be the second selector valve 5 fuel feeding, link manipulation second selector valve 5 in this case, enter from radial direction oil hole 22aa inside first speed that first axial oilhole 221a enters the fluid of the second actuator port B by the second outer radial oilhole 22ab more substantially constant by the first oil suction chamber P1, therefore do not affect luffing action.

6) when the first selector valve 4 valve rod 2 relative to valve body 1 move down distance be greater than d be less than e time, first oil suction chamber P1 and the second oil back chamber T2 is in stronger throttling communicating state, increase with displacement of valve rod is strengthened by throttle, first oil suction chamber P1 and the 3rd oil back chamber T3 also will be in the state of blocking by the indirect communication of the second oil back chamber T2, the fluid of the second oil suction chamber P2 opens the first one-way valve 3, and by entering the second actuator port B by the first guiding gutter 211, if link manipulation second selector valve 5 in this case, its situation and step 5) substantially identical, therefore, it is possible to ensure the stability of flow of the second actuator port B.

7) when the valve rod 2 of the first selector valve 4 moves down apart from when being just greater than e relative to valve body 1, after the oil pressure of the second oil suction chamber P2 reaches the cracking pressure of the first one-way valve, effective flow area that second oil suction chamber P2 enters the second actuator port B by the first one-way valve 3 will increase suddenly, but due to the connection effect of the first valve rod runner 22a, the pressure of the first oil suction chamber P1 and the second actuator port B is close to equal, so, the unexpected increase that now the second oil suction chamber P2 enters effective flow area of the second actuator port B by the second one-way valve 3 can not produce too large impact to the second actuator port B.

8) when the first selector valve 4 valve rod 2 relative to valve body 1 move down distance be greater than f be less than g time, now, the first oil suction chamber P1 is truncated with the runner that is communicated with of the 4th oil back chamber T4 by the second valve rod runner 22b.The fluid of oil inlet P will all enter the second actuator port B by the second oil suction chamber P2, the first guiding gutter 211, and manipulation second selector valve 5 that links in this case will not have an impact to the action of the first selector valve 4.

Valve rod 2 more than in conjunction with the first selector valve 4 moves down relative to valve body 1, working procedure when namely hydraulicdirectional control valve is switched to upper work from meta, when valve rod 2 moves up, substantially identical with above-mentioned state, will repeat no more at this.

To sum up, by arranging valve rod runner 22, hydraulicdirectional control valve provided by the invention and hydraulicdirectional control valve group can not only solve shock problem, and can solve the acceleration problem of actuator, have higher practicability and promotional value.

Below the preferred embodiment of the present invention is described in detail by reference to the accompanying drawings; but; the present invention is not limited to the detail in above-mentioned mode of execution; within the scope of technical conceive of the present invention; can carry out multiple simple variant to technological scheme of the present invention, these simple variant all belong to protection scope of the present invention.

It should be noted that in addition, each concrete technical characteristics described in above-mentioned embodiment, in reconcilable situation, can be combined by any suitable mode, in order to avoid unnecessary repetition, the present invention illustrates no longer separately to various possible compound mode.

In addition, also can carry out combination in any between various different mode of execution of the present invention, as long as it is without prejudice to thought of the present invention, it should be considered as content disclosed in this invention equally.

Claims (14)

1. a hydraulicdirectional control valve, comprise valve body (1) and valve rod (2), described valve body (1) is formed with many inner flow passages (11), the valve opening (12) being communicated with these many inner flow passages (11) and the filler opening (P) be communicated with respective inner runner (11), return opening (T) and actuator port (AB), the outside of described valve rod (2) is formed with guiding gutter (21), and described valve rod (2) can move axially with conducting or end corresponding described inner flow passage (11) in described valve opening (12), thus described hydraulicdirectional control valve is switched between different operating position, and the working position of described hydraulicdirectional control valve comprises meta, at this meta, the hydraulic oil of described hydraulicdirectional control valve can oil return, it is characterized in that, described valve rod (2) inside is formed with valve rod runner (22), described valve rod runner (22) comprises the axial oilhole (221) and radial direction oil hole (222) that are interconnected, described axial oilhole (221) extends along the axis of described valve rod (2), described radial direction oil hole (222) is positioned at the opposite end of described axial oilhole (221) and hydraulic fluid port corresponding to described hydraulicdirectional control valve is respectively communicated with, when switching from meta to other working positions, this valve rod runner (22) can be communicated with described filler opening (P) and the corresponding described actuator port (AB) by this filler opening (P) fuel feeding, or described filler opening (P) and described return opening (T) can be communicated with.

2. hydraulicdirectional control valve according to claim 1, it is characterized in that, when switching from described meta to other working positions, described valve rod runner (22) is communicated with described filler opening (P) and corresponding described actuator port (AB) prior to described guiding gutter (21).

3. according to the hydraulicdirectional control valve in claim 1 or 2 described in any one, it is characterized in that, when switching from described meta to other working position, described valve rod (2) moves along a corresponding axial direction, now, described valve rod runner (22) is communicated with described filler opening (P) and corresponding described actuator port (AB); When switching from described meta to another other working position, described valve rod (2) moves along contrary axial direction, now, described valve rod runner (22) can be communicated with described filler opening (P) and described return opening (T), and along with the movement of described valve rod (2), when being switched to another other working positions described, described valve rod runner (22) can disconnect being communicated with of described filler opening (P) and described return opening (T) gradually.

4. hydraulicdirectional control valve according to claim 3, it is characterized in that, described hydraulicdirectional control valve is three position directional valve, described actuator port (AB) comprises the first actuator port (A) and the second actuator port (B), described valve rod runner (22) correspondingly comprises the first valve rod runner (22a) and the second valve rod runner (22b) that are respectively formed at described valve rod (2) inside, described first valve rod runner (22a) is for being communicated with described filler opening (P) and described second actuator port (B), described second valve rod runner (22b) is for being communicated with described filler opening (P) and described first actuator port (A).

5. hydraulicdirectional control valve according to claim 4, is characterized in that, described valve body (1) is also formed with the oil outlet (P3) for oil return.

6. hydraulicdirectional control valve according to claim 5, it is characterized in that, the second oil back chamber (T2) of being communicated with described oil outlet (P3) and the 3rd oil back chamber (T3), the first oil suction chamber (P1) of being communicated with described filler opening (P) and the second oil suction chamber (P2) and the first oil back chamber (T1) be communicated with described return opening (T) and the 4th oil back chamber (T4) is formed in described valve body (1)

When described hydraulicdirectional control valve is positioned at meta, described first oil suction chamber (P1) is communicated with described 3rd oil back chamber (T3) with described second oil back chamber (T2) simultaneously, at described hydraulicdirectional control valve from meta to the process that other working positions switch, first described first oil suction chamber (P1) can be communicated with corresponding described first actuator port (A) or described second actuator port (B) by the described valve rod runner (22) that described valve rod (2) is inner, then described second oil suction chamber (P2) can be communicated with described first actuator port (A) or described second actuator port (B) by the described guiding gutter (21) that described valve rod (2) is outside.

7. hydraulicdirectional control valve according to claim 6, it is characterized in that, described second oil back chamber (T2) and described 3rd oil back chamber (T3) are respectively formed at the axial both sides of described first oil suction chamber (P1), described first oil back chamber (T1) is formed in the axially outside of described second actuator port (B), described 4th oil back chamber (T4) is formed in the axially outside of described first actuator port (A)

The described guiding gutter (21) of described valve rod (2) outside comprises the first guiding gutter (211), the second guiding gutter (212), the 3rd guiding gutter (213) and the 4th guiding gutter (214) arranged vertically successively

Described first valve rod runner (22a) comprise be positioned at axially inner side first inside radial direction oil hole (22aa), be positioned at the first outer radial oilhole (22ab) in axially outside and be communicated with the first axial oilhole (221a) of this radial direction oil hole (22aa) and the first outer radial oilhole (22ab) inside first, described second valve rod runner (22b) comprise be positioned at axially inner side second inside radial direction oil hole (22ba), be positioned at the second outer radial oilhole (22bb) in axially outside and be communicated with the second axial oilhole (221b) of this second outer radial oilhole (22ba) and the second outer radial oilhole (22bb),

The outside of described valve rod (2) is also formed and is positioned at the axial both sides of described first guiding gutter (211) and the first segment chute (23) be communicated with this first guiding gutter (211), and be positioned at described 4th guiding gutter (214) axial both sides and the second section chute (24) be communicated with the 4th guiding gutter (214), inside described first, inside radial direction oil hole (22aa) and described second, radial direction oil hole (22ba) lays respectively in described second guiding gutter (212) and described 3rd guiding gutter (213)

Described inner flow passage (11) in described valve body (1) comprises the first inner flow passage (111) and the second inner flow passage (112) that are communicated with described second oil suction chamber (P2) and described valve opening (12) respectively, and be communicated with the 3rd inner flow passage (113) of described first actuator port (A) and described valve opening (12) and be communicated with the 4th inner flow passage (114) of described second actuator port (B) and described valve opening (12)

When described meta, described first outer radial oilhole (22ab) and described second outer radial oilhole (22bb) are the first length (a) with the axial distance of described first oil back chamber (T1) and described 4th oil back chamber (T4) respectively, be the second length (b) with the axial distance of described 3rd inner flow passage (113) and described 4th inner flow passage (114) respectively, the inner side cut-off end of described second guiding gutter (212) and described 3rd guiding gutter (213) is the 3rd length (c) with the axial distance at the edge of described first oil suction chamber (P1) respectively, the inner of the inner and described second section chute (24) of described first segment chute (23) is the 4th length (d) with the axial distance of described first inner flow passage (111) and the second inner flow passage (112) respectively, described first guiding gutter (211) and described 4th guiding gutter (214) are the 5th length (e) with the axial distance of described first inner flow passage (111) and the second inner flow passage (112) respectively

Wherein, described first length (a), described second length (b), described 3rd length (c), described 4th length (d) and described 5th length (e) become large successively.

8. hydraulicdirectional control valve according to claim 7, it is characterized in that, when described meta, the outside cut-off end of described second guiding gutter (212) and described 3rd guiding gutter (213) is the 6th length (f) with the axial distance at described second oil back chamber (T2) and described 3rd oil back chamber (T3) edge respectively, and described 6th length (f) is greater than described 5th length (e).

9. a hydraulicdirectional control valve group, comprises multiple interconnective selector valve, it is characterized in that, one of them described selector valve is the hydraulicdirectional control valve in claim 1-4 described in any one.

10. a hydraulicdirectional control valve group, comprises multiple interconnective selector valve, it is characterized in that, one of them described selector valve is the hydraulicdirectional control valve in claim 5-8 described in any one.

11. hydraulicdirectional control valve groups according to claim 10, it is characterized in that, described multiple selector valve comprises the first selector valve (4) and the second selector valve (5), described first selector valve (4) is described hydraulicdirectional control valve, described second selector valve (5) is three six-way transfer valves, the described oil outlet (P3) of described first selector valve is communicated with described second selector valve (5), when described second selector valve (5) is positioned at meta, described oil outlet (P3) is by the oil return of described second selector valve (5), when other working positions, described oil outlet (P3) is ended by described second selector valve (5).

12. 1 kinds of engineering machinery, this project machinery comprises multiple actuator and controls the main reversing valve (6) of the plurality of actuator action, and it is characterized in that, described main reversing valve is the hydraulicdirectional control valve group described in claim 9 or 10.

13. engineering machinery according to claim 12, it is characterized in that, described engineering machinery is hoist, this hoist comprises amplitude oil cylinder, hoist motor and control the described main reversing valve (6) of this amplitude oil cylinder and hoist motor action, described main reversing valve (6) comprises the first selector valve (4) controlling described amplitude oil cylinder, and control second selector valve (5) of described hoist motor, and be provided with the second one-way valve (7) between described first selector valve (4) and described second selector valve (5), this second one-way valve (7) allows fluid to flow to described second selector valve (5) from described first selector valve (4).

14. engineering machinery according to claim 13, it is characterized in that, described first selector valve (4) is described hydraulicdirectional control valve, described second selector valve (5) is three six-way transfer valves, described valve body (1) is also formed with the oil outlet (P3) for oil return, the described oil outlet (P3) of described first selector valve is communicated with described second selector valve (5), when described second selector valve (5) is positioned at meta, described oil outlet (P3) is by the oil return of described second selector valve (5), when other working positions, described oil outlet (P3) is ended by described second selector valve (5).