CN103225633A

CN103225633A - Hydraulic reversing valve, hydraulic reversing valve group and engineering machinery

Info

Publication number: CN103225633A
Application number: CN2013101682766A
Authority: CN
Inventors: 刘先爱; 潘文华
Original assignee: Changde Zhonglian Zhongke Hydraulic Co ltd; Zoomlion Heavy Industry Science and Technology Co Ltd
Current assignee: Changde Zhonglian Zhongke Hydraulic Co ltd; Zoomlion Heavy Industry Science and Technology Co Ltd
Priority date: 2013-05-09
Filing date: 2013-05-09
Publication date: 2013-07-31
Anticipated expiration: 2033-05-09
Also published as: CN103225633B

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 the engineering machinery of using this hydraulicdirectional control valve group.

Background technique

In engineering machinery field, can use the hydraulicdirectional control valve group usually, use for convenience will be designed to integrated compound valve member, i.e. multiple directional control valve as the hydraulicdirectional control valve group of main reversing valve usually.With the hoist is example, in its main reversing valve, generally includes the hydraulicdirectional control valve of control jib luffing and elevator folding and unfolding.These two selector valves interconnect, with the jib luffing operation of finishing hoist respectively and the folding and unfolding operation of elevator, particularly, a selector valve is controlled arm support oil cylinder, and another then controls hoist motor, when two selector valves did not all commutate, the oil-feed fluid of the selector valve of control arm support oil cylinder carried out oil return by the selector valve of control hoist motor.Wherein, as single selector valve,, the useful area of each hydraulic fluid port can cause impact to executive component because undergoing mutation.For example; in selector valve with meta oil return function; through regular meeting occur hydrovalve from meta to the process that other working positions switch; because filler opening need be to actuator port supply pressure oil; need the valid circulation area of its oil return to diminish; and can sport very little in a flash at certain; this will make the pressure of filler opening increase suddenly; thereby can impact to the corresponding work hydraulic fluid port in this moment; then cause the impact of executive component; for example arm support oil cylinder is caused greater impact, this can also can have a negative impact to the service behaviour of engineering machinery.

In addition, in the hydraulicdirectional control valve group, when moving simultaneously in a plurality of actuators, because corresponding a plurality of selector valves interconnect, the actuator of back action can cause formerly that action actuating mechanism quickens suddenly.For example, when the selector valve of control amplitude oil cylinder action is in the transition position, the oil-feed fluid part of this selector valve can be by the selector valve oil return of control hoist motor, another part is given the amplitude oil cylinder fuel feeding, if operate hoist motor this moment simultaneously, to control the oil return of the selector valve of amplitude oil cylinder in the time of can operating owing to the selector valve of control hoist motor partly blocks, and make in this controls the selector valve of amplitude oil cylinder in a flash filler opening strengthen suddenly to the flow of actuator port, this unexpected accelerating process can cause jib luffing velocity jump and cause jib to rock, not only influence the operating characteristics of engineering machinery, but also cause unnecessary accident easily.

Therefore, provide a kind of hydraulicdirectional control valve and hydraulicdirectional control valve group that can solve above-mentioned a kind of problem at least that controlling of engineering machinery had 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 can be reduced at least from the degree of meta impact of generation when other working positions switch.

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

A further object of the present invention provides 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 that is communicated with the respective inner runner, return opening and actuator port, the outside of described valve rod is formed with guiding gutter, and described valve rod can move axially in described valve opening with conducting or by corresponding described inner flow passage, thereby make described hydraulicdirectional control valve between the different operating position, switch, 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 valve rod inside is formed with the valve rod runner, from meta when other working positions switch, this valve rod runner can be communicated with described filler opening and by the corresponding described actuator port of this filler opening fuel feeding, perhaps can be communicated with described filler opening and described return opening.

Preferably, described valve rod runner comprises axial oilhole and the radial direction oil hole that is interconnected, described axial oilhole extends axially along described valve rod, and described radial direction oil hole is positioned at the opposite end of described axial oilhole and is communicated with the corresponding hydraulic fluid port of described hydraulicdirectional control valve respectively.

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

Preferably, from described meta when other working position switches, described valve rod moves along a corresponding axial direction, at this moment, described valve rod runner is communicated with described filler opening and corresponding described actuator port; From described meta when another other working positions switch, described valve rod moves along opposite axial direction, at this moment, described valve rod runner can be communicated with described filler opening and described return opening, and along with moving of described valve rod, when switching to described another other working positions, described valve rod runner can disconnect the connection of described filler opening and described return opening gradually.

Preferably, described hydraulicdirectional control valve is a three position directional valve, described actuator port comprises first actuator port and second actuator port, described valve rod runner correspondingly comprises the first valve rod runner and the second valve rod runner that is respectively formed at described valve rod inside, the described first valve rod runner is used to be communicated with described filler opening and described second actuator port, and the described second valve rod runner is used to be communicated with described filler opening and described first actuator port.

Preferably, also be formed with the oil outlet that is used for oil return on the described valve body.

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

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

Preferably, described second oil back chamber and described the 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 on the axial outside of described second actuator port, and described the 4th oil back chamber is formed on the axial outside of described first actuator port

The described guiding gutter of described valve rod outside comprises first guiding gutter, second guiding gutter, the 3rd guiding gutter and the 4th guiding gutter of arranging vertically successively,

The described first valve rod runner comprises the first inboard radial direction oil hole that is positioned at axial inboard, the first axial oilhole that is positioned at the first outer radial oilhole in the axial outside and is communicated with this first inboard radial direction oil hole and the first outer radial oilhole, the described second valve rod runner comprises the second inboard radial direction oil hole that is positioned at axial inboard, the second axial oilhole that is positioned at the second outer radial oilhole in the axial outside and is communicated with this second outer radial oilhole and the second outer radial oilhole

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

Described inner flow passage in the described valve body comprises first inner flow passage and second inner flow passage that is 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 be communicated with the 4th inner flow passage of described second actuator port and described valve opening

When described meta, described first outer radial oilhole and the described second outer radial oilhole are first length with the axial distance of described first oil back chamber and described the 4th oil back chamber respectively, axial distance with described the 3rd runner and described the 4th runner is second length respectively, the inboard of described second guiding gutter and described the 3rd guiding gutter is the 3rd length with the axial distance at the edge of described first oil suction chamber respectively by end, the inner of inner and described second throttling groove of described first segment chute is the 4th length with the axial distance of described first inner flow passage and second inner flow passage respectively, described first guiding gutter and described the 4th guiding gutter are the 5th length with the axial distance of described first inner flow passage and second inner flow passage respectively

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

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

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

Preferably, described a plurality of selector valve comprises first selector valve and 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 was positioned at meta, described oil outlet was by the 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, the main reversing valve that this project machinery comprises a plurality of actuators and controls this a plurality of actuators action, wherein, described main reversing valve is a claim hydraulicdirectional control valve group provided by the invention.

Preferably, described engineering machinery is a hoist, this hoist comprises amplitude oil cylinder, hoist motor and controls this amplitude oil cylinder and the described main reversing valve of hoist motor action, described main reversing valve comprises first selector valve of controlling described amplitude oil cylinder, and second selector valve of controlling described hoist motor, and be provided with 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 the 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, because the valve rod inside of hydraulicdirectional control valve provided by the invention is formed with the valve rod runner, from meta when other working positions switch, pressure jump at the filler opening place, because the existence of valve rod runner, when the valve rod runner is communicated with filler opening and actuator port, the pressure of filler opening and actuator port can keep equal substantially, and when the valve rod runner is communicated with filler opening and return opening, can make unnecessary fluid to the return opening oil return, therefore can not make that the pressure of relevant work hydraulic fluid port increases suddenly, promptly because the buffer function of valve rod runner, only can make the pressure of actuator port raise gradually, thereby reduce the degree that impact takes place.In addition, can also be communicated with filler opening and return opening owing to the invention provides the valve rod runner of the hydraulicdirectional control valve in the hydraulicdirectional control valve group, therefore can guarantee that the flow of actuator port remains unchanged substantially, therefore can reduce the degree that velocity jump takes place at least, therefore, make the practicability of hydraulicdirectional control valve provided by the invention, hydraulicdirectional control valve group and engineering machinery strengthen.

Other features and advantages of the present invention will partly be described in detail in embodiment subsequently.

Description of drawings

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

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

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

Fig. 3 is the sectional structure schematic representation of the line A-A intercepting from Fig. 2.

Description of reference numerals

Embodiment

Below in conjunction with accompanying drawing the specific embodiment of the present invention is elaborated.Should be understood that embodiment described herein only is used for description and interpretation the present invention, is not limited to the present invention.

In the present invention, do not doing under the situation of opposite explanation, the noun of locality that uses is as the benchmark definition with the page of accompanying drawing 2 and Fig. 3 as " upper and lower ", " inside and outside " then is that the axial centre with valve rod is a benchmark, corresponding part is inboard near a side of this axial centre, and be the outside away from a side of this axial centre, in addition, " axially and radially " is that length direction with valve rod is the basis definition, the length direction that is valve rod is an axial direction, and radial direction is perpendicular to this length direction.Need to prove that these nouns of locality only are used to illustrate the present invention, are not limited to the present invention.

Need to prove in addition; hydraulic schematic diagram has as shown in Figure 1 just shown the working principle of hydraulicdirectional control valve group provided by the invention; can realize that to those skilled in the art the hydraulicdirectional control valve group of above-mentioned working principle can be designed as the multiple directional control valve of integrated combination valve form; can also be designed to drop in protection scope of the present invention for this mode of texturing by the form of pipeline with single valve member connection.

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

In order to solve the above problems, the present invention at first provides a kind of improved hydraulicdirectional control valve, as shown in Figures 2 and 3, this pilot operated directional control valve comprises valve body 1 and valve rod 2, 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 the oil inlet P that is communicated with respective inner runner 11, oil return inlet T and actuator port AB, and wherein those skilled in the art can know the 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 finish the oil return of actuator by another actuator port, for example in preferred implementation of the present invention, in order to control the luffing of arm support oil cylinder, the first actuator port A of hydraulicdirectional control valve can be connected the rod chamber and the rodless cavity of amplitude oil cylinder respectively with the second actuator port B, thereby finishes corresponding luffing operation.In addition, the implication of the oil inlet P of the selector valve hydraulic fluid port that to be this selector valve directly or indirectly be communicated with oil hydraulic pump equal pressure oil sources, to obtain working pressure oil, the implication of the oil outlet T hydraulic fluid port that then to be this selector valve directly or indirectly be communicated with oil sump tank, not driving 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 in valve opening 12 with conducting or by corresponding each inner flow passage 11, particularly, hydraulicdirectional control valve provided by the invention is a spool-type valves, valve rod 2 outsides are 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 can pass through the corresponding inner flow passage 11 of groove part conducting, and by the convex shoulder by corresponding inner flow passage 11, thereby make oil inlet P can be communicated with different actuator port AB with oil return inlet T.Thereby by finish the circulation of hydraulic pressure wet goods fluid in valve body, by or state such as commutation realize that hydraulicdirectional control valve switches between the different operating position, for example realize stretching out or operating mode such as withdrawal 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 too much and give unnecessary details at this.

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, so that actuator does not work, also can be from actuator port AB oil return, so that the off-load of corresponding actuator.Therefore provide in order to solve in the background technique because at the shock problem that when other working positions switch, takes place from meta, in hydraulicdirectional control valve provided by the invention, valve rod 2 inside are formed with valve rod runner 22, and from meta when other working positions switch, this valve rod runner 22 can be communicated with oil inlet P and at least by the relevant work hydraulic fluid port AB of this oil inlet P fuel feeding.Therefore, because the existence of valve rod runner 22, can under some state, oil inlet P and corresponding work hydraulic fluid port AB be communicated with, thereby make the pressure of oil inlet P and actuator port AB to keep equal substantially, therefore even when oil inlet P enters the valid circulation area of relevant work hydraulic fluid port AB change is big suddenly by guiding gutter 21 and inner flow passage 11, oil inlet P can not take place yet to the unexpected situation about increasing of the pressure of relevant work hydraulic fluid port AB, promptly, because the buffer function of valve rod runner 22, only can make the pressure of corresponding work hydraulic fluid port AB raise gradually, thereby can reduce at least the degree of impact taking place, and makes the practicability of hydraulicdirectional control valve group provided by the invention and engineering machinery strengthen.Need to prove that when valve rod runner 22 was in meta at this hydraulicdirectional control valve, the hydraulic oil in this valve rod was in the state of blocking, promptly the pressure oil at filler opening place can not be communicated to actuator port AB through valve rod runner 22 at this moment.

Wherein, preferably, this hydraulicdirectional control valve from meta when other working positions switch, when promptly hydraulicdirectional control valve was in the transition position, valve rod runner 22 was communicated with oil inlet P and corresponding work hydraulic fluid port AB prior to inner flow passage 11 and guiding gutter 21.Can avoid when the guiding gutter 21 that passes through valve rod 2 outsides and inner flow passage 11 direct connection oil inlet P and corresponding work hydraulic fluid port AB, so that the buffer function of valve rod runner 22 is more obvious like this greater impact of actuator port AB.

In addition as a kind of replacement scheme, 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 therefore the sudden change of the valid circulation area of meta oil return is to very little, unnecessary fluid also can be by valve rod runner 22 to the oil return inlet T oil return, oil inlet P can not take place yet to the unexpected situation about increasing of the pressure of relevant work hydraulic fluid port AB, promptly, because the buffer function of valve rod runner 22, only can make the pressure of corresponding work hydraulic fluid port AB raise gradually, thereby can reduce at least the degree of impact taking place, and makes the practicability of hydraulicdirectional control valve group provided by the invention and engineering machinery strengthen.

Wherein, in preferred implementation of the present invention, the effect of optimization and poppet stem runner 22 more, preferably, hydraulicdirectional control valve from meta when other working position switches, valve rod 11 moves along a corresponding axial direction, and at this moment, valve rod runner 22 is communicated with oil inlet P and corresponding work hydraulic fluid port AB; And from meta when another other working positions switch, valve rod 11 moves along opposite axial direction, and at this moment, this valve rod runner 22 can be communicated with oil inlet P and oil return inlet T, and along with moving 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.Promptly, in order to realize that a lot of selector valves have the situation of a plurality of working positions, need to make that the valve rod runner 22 that is opened in valve rod 2 inside itself has two effects, at first when valve rod 2 is mobile facing one direction, can make hydraulicdirectional control valve enter the state of a certain working position, this valve rod runner 22 can be finished above-mentioned connection oil inlet P and the effect of actuator port AB, and when valve rod 2 when another direction moves, can make when hydraulicdirectional control valve enters another working position, along with moving of valve rod 2, same valve rod runner 22 can also play another effect by being communicated with oil inlet P and oil return inlet T: promptly can assist oil inlet P to carry out oil return by the meta drainback passage, make that the unnecessary fluid in oil inlet P place can be by valve rod runner 22 to the oil return inlet T oil return, thereby further guarantee when the valid circulation area of meta drainback passage diminishes suddenly, the unnecessary pressure oil of oil inlet P is by these valve rod runner 22 oil returns, the pressure that makes oil inlet P flow to the fluid of actuator port AB can not undergone mutation, and because moving along with valve rod 2, after this another working position switches fully, this valve rod runner 22 can also disconnect oil inlet P and oil return inlet T gradually, therefore the proper functioning that can not hinder another working position.

It will be appreciated that, hydraulicdirectional control valve from meta when corresponding working position switches, oil inlet P is that throttling is communicated with by valve rod runner 22 and being communicated with of relevant work hydraulic fluid port AB, and throttling action is more and more littler, and when corresponding another work is switching, oil inlet P was communicated with for throttling by valve rod runner 22 and being communicated with also of oil return inlet T, but its throttling action is increasing, it is final when valve rod moves into place, hydraulic oil between blocking-up oil inlet P and the oil return inlet T flows, and therefore just can finally realize the proper functioning of relevant work position.Therefore, by the function that valve rod runner 22 also has auxiliary oil return is set, when can be optimized, make that the performance of valve body is further optimized in the overall structure of valve member.

And more preferably, in three position directional valve, the advantage of this design is the most outstanding.Promptly in preferred implementation of the present 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 is respectively formed at valve rod 2 inside, the first valve rod runner 22a is communicated with the oil inlet P and the second actuator port B, the second valve rod runner 22b is communicated with the oil inlet P and the first actuator port A, particularly, this first valve rod runner 22a and the second valve rod runner 22b lay respectively at the both sides of valve rod 2 axial centre.Since this three position directional valve from meta when switch the different operating position, the movement direction of valve rod 22 is opposite, therefore by above-mentioned two valve rod runners 22, no matter to which working position switch from meta, wherein a valve rod runner 22 can promptly play the effect that is communicated with oil inlet P and relevant work hydraulic fluid port AB, and another valve rod runner 22 then can play the effect that is communicated with oil inlet P and oil return inlet T.Thereby the mode with optimum realizes above-mentioned purpose of the present invention.

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 axial oilhole 221 and the radial direction oil hole 222 that is interconnected, axial oilhole 221 extends axially along valve rod 2, and radial direction oil hole 222 is positioned at the opposite end of described axial oilhole 221 and is communicated with the corresponding hydraulic fluid port of described hydraulicdirectional control valve respectively.Particularly, can be communicated with corresponding oil inlet P, corresponding work hydraulic fluid port AB or corresponding oil return inlet T.That is, axial oilhole 221 by being opened in valve rod inside and the radial direction oil hole at this axial oilhole 221 two ends 222 realize oil inlet P and corresponding work hydraulic fluid port AB, and the connection of realization oil inlet P and oil return inlet T.Particularly, for example process the first valve rod runner 22a and the second valve rod runner 22b in the preferred embodiment for the present invention for convenience, can hole to offer two axial oilholes 221 that do not communicate at the two ends of valve rod 2 at first respectively, thereby hole respectively to offer corresponding radial direction oil hole 222 connection shafts at the sidewall of valve rod 2 then to oilhole 221, in real work, axially shutoff such as plug can be used in the open end of oilhole 221, thereby finish 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 changeable shape, and these distortion all should drop in protection scope of the present invention.

After the functional structure of having introduced the structure of the valve rod runner 22 in the hydraulicdirectional control valve provided by the invention and having prevented to impact, 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 the background technique.

Wherein, in engineering machinery provided by the invention, use main reversing valve 6 to carry out controlling of various executive components usually.This main reversing valve 6 is hydraulicdirectional control valve group provided by the invention, this hydraulicdirectional control valve group comprises interconnective a plurality of selector valve, and wherein, at least one selector valve is a hydraulicdirectional control valve provided by the invention, and at first need to prove, in order to cooperate the use of this hydraulicdirectional control valve group, in hydraulicdirectional control valve provided by the invention, also be formed with oil outlet P3 on the valve body 1 as the meta drainback passage, and be connected with another selector valve by this oil outlet P3, and can realize oil return by the meta of another selector valve by preferably.Particularly, as shown in Figure 1, a plurality of selector valves comprise first selector valve 4 and second selector valve 5, first selector valve 4 is a hydraulicdirectional control valve provided by the invention, second selector valve 5 is three six-way transfer valves, the oil outlet P3 of first selector valve is communicated with second selector valve 5, when first selector valve 4 and second selector valve 5 are positioned at meta, oil outlet P3 is by 5 oil returns of second selector valve, when other working positions, because second selector valve 5 need carry out different work, so oil outlet P3 is then ended by second selector valve 5.The working principle of the working principle of this second selector valve 5 and first selector valve 4 is similar, it mainly passes through oil inlet P ', return opening (the mark, in integrated form combination valve multiple directional control valve, the oil return inlet T of this return opening and 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 for example control of hoist motor of actuator.And preferably, in the control of hoist of the present invention, be provided with second one-way valve 7 between first selector valve 4 and second selector valve 5, this second one-way valve 7 allows fluid to flow to second selector valve 5 from first selector valve 4, with the control of the hoist motor that can finish amplitude oil cylinder, and can realize that double pumps are to the interflow of hoist motor fuel feeding by two selector valves.

In conjunction with among Fig. 1 and Fig. 3 as can be seen, when first selector valve 4 is in the transition position, promptly both some passed through valve rod runner 22 to actuator port AB fuel feeding to the fluid of the oil inlet P of first selector valve 4, some carries out oil return by oil outlet P3 from second selector valve 5 again, this moment is if operate second selector valve 5 simultaneously, the selector valve 4 of winning is blocked by the oil return part of second selector valve 5, unnecessary fluid has the trend that flows to actuator port AB from oil inlet P, if first selector valve 4 does not improve, can make at the corresponding work hydraulic fluid port AB that is fed to first selector valve 4 from meta to the more heavy wool liquid of first selector valve 4 of other working positions switchings, promptly increased the hydraulic fluid flow rate of actuator port, then can cause for example arm support oil cylinder speed increase of actuator of first selector valve, 4 controls, even also can also can suddenly change by flow in a flash at certain.For example in the operation of carrying out the jib luffing, when not improving first selector valve 4 and being in the transition position, when operating the elevator folding and unfolding again, can make that arm support oil cylinder takes place to quicken suddenly by first selector valve 4, this unexpected acceleration will cause hoist that comparatively serious safety problem takes place.

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

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

At first structurally, in order to realize above-mentioned hydraulicdirectional control valve and hydraulicdirectional control valve group, in preferred implementation of the present invention, be formed with the second oil back chamber T2 and the 3rd oil back chamber T3 that are communicated with oil outlet P3 in the valve body 1, the first oil suction chamber P1 that is communicated with oil inlet P and the second oil suction chamber P2, and first oil back chamber T1 that is 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 communicate by oil outlet P3, be that hydraulicdirectional control valve is three six-way transfer valves, and between meta and two working positions, also have corresponding transition working position.Wherein, when hydraulicdirectional control valve is positioned at meta, the first oil suction chamber P1 is communicated with simultaneously with second oil back chamber T2 that lays respectively at its relative both sides and the 3rd oil back chamber T3, promptly realize realizing oil return, and the described second oil back chamber T2 and the 3rd oil back chamber T3 are communicated with the radial direction oil hole 222 of the inboard of two valve rod runners 22 respectively when meta by the meta of oil outlet P3, second one-way valve 7 and second selector valve 5.Hydraulicdirectional control valve from meta to the process that other working positions switch, at first the first oil suction chamber P1 can be communicated with the corresponding first actuator port A or the second actuator port B by the valve rod runner 22 of valve rod 2 inside, and the second oil suction chamber P2 can be communicated with the first actuator port A or the second actuator port B by the inner flow passage 11 and the guiding gutter 21 of valve rod 2 outsides then.Wherein be provided with first one-way valve 3 between the second oil suction chamber P2 and the actuator port AB, so that the second oil suction chamber P2 by guiding gutter 21 with need at first to build the pressure before actuator port AB is communicated with, after equal pressure reaches the cracking pressure of first one-way valve 3, can open first one-way valve 3, pass through guiding gutter 21 again to actuator port AB fuel feeding, the stability of hydraulicdirectional control valve work is provided.

More specifically, as shown in Figures 2 and 3, the second oil back chamber T2 and the 3rd oil back chamber T3 are respectively formed at the axial both sides of the first oil suction chamber P1, the first oil back chamber T1 is formed on the axial outside of the second actuator port B, the 4th oil back chamber T4 is formed on the axial outside of the first actuator port A, the guiding gutter 21 of valve rod outside comprises first guiding gutter of arranging vertically successively 211, second guiding gutter 212, the 3rd guiding gutter 213 and the 4th guiding gutter 214, wherein, described first guiding gutter 211 is used for being communicated with the described second actuator port B, the 4th guiding gutter 214 is used for being communicated with the described first actuator port A, second guiding gutter 212 is arranged between the first oil suction chamber P1 and the second oil back chamber T2 and is used to be communicated with the first oil suction chamber P1 and the second oil back chamber T2, and the 3rd guiding gutter 213 is arranged between the first oil suction chamber P1 and the 3rd oil back chamber T3 and is used to be 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 the described first oil suction chamber P1.The first valve rod runner 22a comprises the first inboard radial direction oil hole 22aa that is positioned at axial inboard, the first axial oilhole 221a that is positioned at the first outer radial oilhole 22ab in the axial outside and is communicated with this first inboard radial direction oil hole 22aa and the first outer radial oilhole 22ab, the second valve rod runner 22b comprises the second inboard radial direction oil hole 22ba that is positioned at axial inboard, be positioned at the second outer radial oilhole 22bb in the axial outside and be communicated with this second outer radial oilhole 22ba and the second axial oilhole 221b of the second outer radial oilhole 22bb, thereby can not only finish 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 can also be finished being communicated with of the first oil suction chamber P1 and the first oil back chamber T1 and the 4th oil back chamber T4.

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

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

Because when meta, the radial direction oil hole 222 of the inboard of two valve rod runners 22 all is communicated with the first oil suction chamber P1, therefore after valve rod 2 begins from meta to move the first length a, can make corresponding valve rod runner 22 be communicated with oil inlet P and oil return inlet T by the radially hydraulic fluid port 222 in the outside, then can be communicated with oil inlet P and corresponding work hydraulic fluid port AB after further moving to the second length b.The outer end of the also preferred in addition first segment chute 23 and second throttling groove 24 also is the second length b with the axial distance of the first oil back chamber T1 and the 4th oil back chamber T4 respectively, therefore when valve rod 2 moves the second length b after, understand disconnection between corresponding work hydraulic fluid port AB and the adjacent oil back chamber and be communicated with.

In addition, the inboard of second guiding gutter 212 and the 3rd guiding gutter 213 is the 3rd length c with the axial distance at the edge of the corresponding first oil suction chamber P respectively by end (i.e. the respective side of the convex shoulder between second guiding gutter 212 and the 3rd guiding gutter 213), therefore, when valve rod 2 move reach the 3rd length c after, the circulation area of second guiding gutter 212 and the first oil suction chamber P1 will diminish suddenly, and making the second oil back chamber T2 disconnect with the first oil suction chamber P1 is communicated with, perhaps the circulation area of the 3rd guiding gutter 213 and the first oil suction chamber P1 diminishes, and makes the 3rd oil back chamber T3 and the first oil suction chamber P1 disconnect.In addition, the inner of inner and second throttling groove 24 of first segment chute 23 is the 4th length d with the axial distance of first inner flow passage 111 and second inner flow passage 112 respectively, promptly when valve rod displacement distance reaches the 4th length d, will begin by the second oil suction chamber P2 to corresponding work hydraulic fluid port AB fuel feeding; And first guiding gutter 211 and the 4th guiding gutter 214 are the 5th length e with the axial distance of first inner flow passage 111 and second inner flow passage 112 respectively, therefore after valve rod moves to the 5th length e, will further increase gradually to the flow of corresponding work hydraulic fluid port AB fuel feeding from the second oil suction chamber P2.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 greatly successively, and promptly this above-mentioned process will take place successively.Therefore summarily, move down with valve rod 22 and to be example, after distance that valve rod 22 moves was 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 distance that valve rod 22 moves was 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 was greater than c, the oil return of oil outlet P3 significantly reduced; Behind d, the second oil suction chamber P2 can begin to the second actuator port B fuel feeding, therefore at a in the process of e, hydraulicdirectional control valve provided by the invention and hydraulicdirectional control valve group can effectively prevent the phenomenon of impacting and quickening.

In addition, also preferably, when meta, the outside of 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 by end, and the 6th length f is greater than the 5th length e.Since valve rod 2 displacement distances greater than e after, flow from the second oil suction chamber P2 to the second actuator port B2 increases gradually, after displacement distance is greater than f, then hydraulicdirectional control valve passes through first guiding gutter 211 to the second actuator port B2 fuel feeding by the second fuel supply chamber P2 fully, the second valve rod runner 22b then is cut off, and disconnects the connection 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, for seven length of expression valve rod 2 to spring seat, also is the range that 2 one working positions of valve rod switch as the g among Fig. 2.

To axially move down with valve rod 2 below, the process of hydraulicdirectional control valve when upwards switch the position from meta introduced the working procedure of hydraulicdirectional control valve provided by the invention and hydraulicdirectional control valve group in detail.

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

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

3) move down distance greater than b during with respect to valve body 1 when the valve rod 2 of first selector valve 4 less than c, the first oil suction chamber P1 and the second oil back chamber T2 are in stronger throttling communicating state, also will be in stronger throttle with the 3rd oil back chamber T3, and throttle will be strengthened with the increase of valve rod 2 displacements, the second actuator port B was blocked with being communicated with of the first oil back chamber T1, fluid enters the first axial oilhole 221a by the first inboard radial direction oil hole 22aa, and enter actuator port B by the first outer radial oilhole 22ab, after reaching certain value, oil pressure can promote amplitude oil cylinder work, under this state, handle second selector valve 5 if link, the first oil suction chamber P1 will enter the second axial oilhole 221b by the second inboard radial direction oil hole 22ba by the fluid that enters the 3rd oil back chamber T3, enter the 4th oil back chamber T4 through the second outer radial oilhole 22bb again, thereby flow back to oil return inlet T.When if the induced pressure of second selector valve 5 is low, also can some fluid by second one-way valve 7 and the oil inlet P ' the fluid interflow that provides is second selector valve, 5 fuel feeding, in a word, second selector valve 5 is handled in interlock under this state, entering the first axial oilhole 221a by the first oil suction chamber P1 from the first inboard radial direction oil hole 22aa, to enter the speed of fluid of the second actuator port B by the first outer radial oilhole 22ab more constant substantially, so do not influence the luffing action;

4) move down distance just c will have been reached the time with respect to valve body 1 when the valve rod 2 of first selector valve 4, the first oil suction chamber P1 will reduce suddenly by effective flow area that restriction enters the 3rd oil back chamber T3, the pressure of the first oil suction chamber P1 will increase suddenly, but because the buffer function of the first valve rod runner 22a, the first oil suction chamber P1 enters the increase that the oil pressure of the second actuator port B will be gradually by the first inboard radial direction oil hole 22aa, the first axial oilhole 221a, the first outer radial oilhole 22ab, thereby can not produce too big impact at the second actuator port B;

5) move down distance greater than c during with respect to valve body 1 when the valve rod 2 of first selector valve 4 less than d, the first oil suction chamber P1 and the second oil back chamber T2 are in stronger throttling communicating state, throttle will be strengthened with the increase of valve rod 2 displacements, the direct state of blocking that is in that is communicated with of the first oil suction chamber P1 and the 3rd oil back chamber T3, the fluid part of the first oil suction chamber P1 is entered the first axial oilhole 221a and is entered the second actuator port B by the first outer radial oilhole 22ab by the first inboard radial direction oil hole 22aa, after reaching certain value, oil pressure can promote amplitude oil cylinder work, 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 are in communicating state with oil outlet P3 all the time, under this state, handle second selector valve 5 if link, the first oil suction chamber P1 will enter the second axial oilhole 221b by the restriction of the second oil back chamber T2 by the second inboard radial direction oil hole 22ba to the part fluid of the 3rd oil back chamber T3, enter oil return inlet T through the second outer radial oilhole 22bb again, when if the induced pressure of second selector valve 5 is low than oil outlet P3, also can some fluid by second one-way valve 7 and the oil inlet P ' the fluid interflow that provides is second selector valve, 5 fuel feeding, second selector valve 5 is handled in interlock under this state, entering the first axial oilhole 221a by the first oil suction chamber P1 from the first inboard radial direction oil hole 22aa, to enter the speed of fluid of the second actuator port B by the second outer radial oilhole 22ab more constant substantially, so do not influence the luffing action.

6) move down distance greater than d during with respect to valve body 1 when the valve rod 2 of first selector valve 4 less than e, the first oil suction chamber P1 and the second oil back chamber T2 are in stronger throttling communicating state, throttle will be strengthened with the increase of displacement of valve rod, the 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 is opened first one-way valve 3, and by entering the second actuator port B by first guiding gutter 211, under this state, handle second selector valve 5 if link, its situation and step 5) are basic identical, therefore can guarantee the stability of flow of the second actuator port B.

7) move down distance when just being greater than e with respect to valve body 1 when the valve rod 2 of first selector valve 4, after the oil pressure of the second oil suction chamber P2 reaches the cracking pressure of first one-way valve, the second oil suction chamber P2 will increase suddenly by effective flow area that first one-way valve 3 enters the second actuator port B, but because the connection effect of the first valve rod runner 22a, the first oil suction chamber P1 equates with the pressure of the second actuator port B is approaching, so the unexpected increase that this moment, the second oil suction chamber P2 entered effective flow area of the second actuator port B by second one-way valve 3 can not produce too big impact to the second actuator port B.

8) move down distance greater than f during less than g with respect to valve body 1 when the valve rod 2 of first selector valve 4, at this moment, the first oil suction chamber P1 is blocked 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, first guiding gutter 211, and the action of 5 pairs first selector valves 4 of interlock manipulation second selector valve will not exert an influence under this state.

Above valve rod 2 in conjunction with first selector valve 4 moves down with respect to valve body 1, and promptly the working procedure of hydraulicdirectional control valve when meta switches to upper work is basic identical with above-mentioned state when valve rod 2 moves up, and will repeat no more at this.

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

Below describe preferred implementation of the present invention in conjunction with the accompanying drawings in detail; but; the present invention is not limited to the detail in the above-mentioned mode of execution; in technical conceive scope 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.

Need to prove in addition, each concrete technical characteristics described in above-mentioned embodiment under reconcilable situation, can make up by any suitable manner, for fear of unnecessary repetition, the present invention is to the explanation no longer separately of various possible compound modes.

In addition, also can carry out combination in any between the various 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

1. hydraulicdirectional control valve, comprise valve body (1) and valve rod (2), described valve body (1) is formed with many inner flow passages (11), be communicated with valve opening (12) of these many inner flow passages (11) and the filler opening (P) that is 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 in described valve opening (12) with conducting or by corresponding described inner flow passage (11), thereby make described hydraulicdirectional control valve between the different operating position, switch, 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), from meta when other working positions switch, this valve rod runner (22) can be communicated with described filler opening (P) and by the corresponding described actuator port (AB) of this filler opening (P) fuel feeding, perhaps can be communicated with described filler opening (P) and described return opening (T).

2. hydraulicdirectional control valve according to claim 1, it is characterized in that, described valve rod runner (22) comprises axial oilhole (221) and the radial direction oil hole (222) that is interconnected, described axial oilhole (221) extends axially along described valve rod (2), and described radial direction oil hole (222) is positioned at the opposite end of described axial oilhole (221) and is communicated with the corresponding hydraulic fluid port of described hydraulicdirectional control valve respectively.

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

4. according to any described hydraulicdirectional control valve among the claim 1-3, it is characterized in that, from described meta when other working position switches, described valve rod (11) moves along a corresponding axial direction, at this moment, described valve rod runner (22) is communicated with described filler opening (P) and corresponding described actuator port (AB); From described meta when another other working positions switch, described valve rod (11) moves along opposite axial direction, at this moment, described valve rod runner (22) can be communicated with described filler opening (P) and described return opening (T), and along with moving of described valve rod (2), when switching to described another other working positions, described valve rod runner (22) can disconnect the connection of described filler opening (P) and described return opening (T) gradually.

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

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

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

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

8. hydraulicdirectional control valve according to claim 7, it is characterized in that, described second oil back chamber (T2) and described the 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 on the axial outside of described second actuator port (B), described the 4th oil back chamber (T4) is formed on the axial outside of described first actuator port (A)

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

The described first valve rod runner (22a) comprises the first inboard radial direction oil hole (22aa) that is positioned at axial inboard, the first axial oilhole (221a) that is positioned at the first outer radial oilhole (22ab) in the axial outside and is communicated with this first inboard radial direction oil hole (22aa) and the first outer radial oilhole (22ab), the described second valve rod runner (22b) comprises the second inboard radial direction oil hole (22ba) that is positioned at axial inboard, the second axial oilhole (221b) that is positioned at the second outer radial oilhole (22bb) in the axial outside and is communicated with this second outer radial oilhole (22ba) and the second outer radial oilhole (22bb)

Described valve rod, (2) outside also is formed with and is positioned at described first guiding gutter, (211) axially both sides and with this first guiding gutter, (211) the first segment chute of Lian Tonging, (23), and be positioned at described the 4th guiding gutter, (214) axially both sides and with the 4th guiding gutter, (214) second throttling groove of Lian Tonging, (24), the described first inboard radial direction oil hole, (22aa) with the described second inboard radial direction oil hole, (22ba) lay respectively at described second guiding gutter, (212) and described the 3rd guiding gutter, (213) in

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

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

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

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

10. a hydraulicdirectional control valve group comprises a plurality of interconnective selector valves, it is characterized in that, one of them described selector valve is any described hydraulicdirectional control valve among the claim 1-5.

11. a hydraulicdirectional control valve group comprises a plurality of interconnective selector valves, it is characterized in that, one of them described selector valve is any described hydraulicdirectional control valve among the claim 6-9.

12. hydraulicdirectional control valve group according to claim 11, it is characterized in that, described a plurality of selector valve comprises first selector valve (4) and 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), at described second selector valve (5) when being positioned at meta, described oil outlet (P3) is by described second selector valve (5) oil return, when other working positions, described oil outlet (P3) is ended by described second selector valve (5).

13. the main reversing valve (6) that an engineering machinery, this project machinery comprise a plurality of actuators and control this a plurality of actuators action is characterized in that described main reversing valve is claim 10 or 11 described hydraulicdirectional control valve groups.

14. engineering machinery according to claim 13, it is characterized in that, described engineering machinery is a hoist, this hoist comprises amplitude oil cylinder, hoist motor and control this amplitude oil cylinder and the described main reversing valve (6) of hoist motor action, described main reversing valve (6) comprises first selector valve (4) of controlling described amplitude oil cylinder, and second selector valve (5) of controlling described hoist motor, and be provided with 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).

15. engineering machinery according to claim 14, 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, the described oil outlet (P3) of described first selector valve is communicated with described second selector valve (5), at described second selector valve (5) when being positioned at meta, described oil outlet (P3) is by described second selector valve (5) oil return, when other working positions, described oil outlet (P3) is ended by described second selector valve (5).