CN102678645A - Direct-acting overflow valve, direct-acting overflow valve group and hydraulic overflow loop - Google Patents
Direct-acting overflow valve, direct-acting overflow valve group and hydraulic overflow loop Download PDFInfo
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- CN102678645A CN102678645A CN2012101750684A CN201210175068A CN102678645A CN 102678645 A CN102678645 A CN 102678645A CN 2012101750684 A CN2012101750684 A CN 2012101750684A CN 201210175068 A CN201210175068 A CN 201210175068A CN 102678645 A CN102678645 A CN 102678645A
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Abstract
The invention discloses a direct-acting overflow valve, comprising a remote control opening (V) and a hydraulic oil counteractive cavity (X) communicated with the remote control opening (V), wherein the hydraulic oil counteractive cavity (X) is communicated with an oil inlet (P); the hydraulic oil in the hydraulic oil counteractive cavity (X) acts on a valve core (102) in the same direction as the spring acts on a valve core (10); the hydraulic oil on an oil inlet pressure surface has an effective area more than the hydraulic oil on the pressure surface of the valve core (102) exposed in the hydraulic oil counteractive cavity (X). Additionally, the invention also provides a direct-acting overflow valve group comprising the direct-acting overflow valve, and a hydraulic overflow loop. As the remote control opening is added in the direct-acting overflow valve, the direct-acting overflow valve has an unloading function. Meanwhile, with the adoption of the direct-acting overflow valve, the functions of overflowing with low flow and unloading with high flow are realized when the overflowing and unloading functions are realized due to the more optimized structural design.
Description
Technical field
The present invention relates to a kind of relief valve, particularly, relate to a kind of direct-acting overflow valve.In addition, the invention still further relates to a kind of direct-acting overflow valve valve group and hydraulic pressure skimmer circuit that comprises said direct-acting overflow valve.
Background technique
Relief valve is a kind of hydraulic control valve commonly used in the hydraulic system; It can be used for the maximum pressure of controlled hydraulic system on the hydraulic system working connection; The working oil path that also can be used for certain hydraulic actuator (for example oil hydraulic cylinder) is to control the working pressure of this actuator.Relief valve mainly is divided into direct-acting overflow valve and pilot operated compound relief valve; Wherein direct-acting overflow valve has simple in structure; Processing cost is lower, advantage such as be active in one's movements, but there is certain narrow limitation in existing direct-acting overflow valve structure owing to self on using.
Particularly, for the sake of security, the relief valve of band remote control port (those skilled in the art are also referred to as " telecontrol mouth ") is installed all in most of hydraulic systems of engineering machinery, generally passes through the hydraulic oil oil pressure of electromagnetic valve remote control port.For example, when the arm of truck crane with respect to the horizontal plane was in less angle, arm position of centre of gravity and pivoting support centre distance were far away, and hoist is to the arm direction trend grow that topples.If operator carry out the luffing operation; When the angle of arm direction and horizontal plane is dangerous less than setting value; Controller can send electrical signal and make the remote control port decompression of secondary relief valve of corresponding filler opening of luffing selector valve; And then make the secondary relief valve be in unloading condition (promptly gushing the hydraulic oil on the working oil path), realize the safety protection effect.
But the relief valve that can play the off-load effect with remote control port all is a pilot operated compound relief valve usually, and Fig. 1 is the pilot operated compound relief valve of typical band remote control port.As shown in Figure 1, the pilot operated compound relief valve of traditional band remote control port plays off-load and does the time spent, remote control port V decompression, thereby main valve plug spring chamber decompression, and the oil pressure of oil inlet P overcomes spring force and promotes main valve plug realization off-load effect.Realizing that overflow effect and off-load do the time spent, its main valve plug all can move to limit position, that is to say that when overflow the opening with its main valve plug when the off-load is the same.When off-load, can lay down fully if guarantee the hydraulic oil on the working oil path so, then the opening of main valve plug must be enough big.This also causes the opening of main valve plug when overflow can be bigger.Play level pressure on the working oil path and do the time spent when this relief valve is installed in, if working pressure reaches setting pressure, have more oil spill stream, the flow on the working oil path also can reduce.Can cause the movement speed of actuator slack-off like this, system's heating, efficient reduces.Simultaneously, known ground, the structure of pilot operated compound relief valve is comparatively complicated, and processing cost is higher, and can there be certain retardation phenomenon in speed of response simultaneously.
China utility application CN2086355U discloses the directly moving relief valve of a kind of differential pressure type; Shown in Figure 2 is the directly moving relief valve of the disclosed differential pressure type of this utility application; It is to be noted at this; The directly moving relief valve of this differential pressure type does not only have remote control port, no unloading function, and can't realize from the relief function that hydraulic principle is analyzed even it is basic yet, referring to shown in Figure 2; The directly moving relief valve of this differential pressure type is through pressure balance valve pocket 13 and the spool 10 common valve internal pressure chambeies that form; And through being formed on throttle orifice makes said internal pressure chamber be communicated with the inlet opening 19 of relief valve on the spool 10, there is difference in areas in the hydraulic oil active area that the hydraulic oil of the hydraulic oil active area of all not mentioned upper-end surface that is in the spool 10 in the said valve internal pressure chamber and inlet opening 19 acts on the lower end conical surface of spool 10 in the full text of this application file, from concrete structure shown in Figure 2; Can only think that the hydraulic oil active area of upper-end surface of spool 10 equates with the hydraulic oil active area of the lower end conical surface of spool 10; Under this situation, because the incompressibility of hydraulic oil, when oil pressure moment of 19 hydraulic oil increases in the inlet opening; Spool 10 has the trend that moves upward; Hydraulic oil moment in said valve internal pressure chamber is compressed, and the oil pressure of the hydraulic oil in it also can rise moment, because the hydraulic oil active area of the upper-end surface of spool 10 equates with the hydraulic oil active area of the lower end conical surface of spool 10; Therefore the oil pressure of the hydraulic oil in said valve internal pressure chamber only need rise to the oil pressure at 19 places, inlet opening and equate; Just the suffered thrust in lower end surface that can balance valve core 10, under this situation because the oil pressure in said valve internal pressure chamber equates that with the oil pressure at 10 places, inlet opening so the hydraulic oil in the valve internal pressure chamber can't be via the throttle orifice on the spool 10 to inlet opening 19 backflows.Therefore, only from the disclosed technology contents of this utility application CN2086355U, the directly moving relief valve of this differential pressure type is generally speaking actual to be rigidity, and it can not realize the differential pressure relief function, more can not realize unloading function via remote control port.
In view of this, need a kind of novel direct-acting overflow valve of design,, thereby widen the application area of direct-acting overflow valve so that this direct-acting overflow valve has the unloading function via remote control port.
Summary of the invention
Technical problem to be solved by this invention provides a kind of direct-acting overflow valve, and this direct-acting overflow valve not only can be realized relief function effectively, and can be used in the realization unloading function.
Further, technical problem to be solved by this invention provides a kind of direct-acting overflow valve, and this direct-acting overflow valve not only can be used in the realization unloading function, and can realize big flow off-load, small flow overflow.
The technical problem that the present invention also will solve provides a kind of direct-acting overflow valve valve group, and this direct-acting overflow valve group not only can realize relief function effectively, and can realize unloading function.
In addition, this invention technical problem to be solved provides a kind of hydraulic pressure skimmer circuit, and this hydraulic pressure skimmer circuit not only can be realized relief function effectively, and can realize unloading function.
In order to solve the problems of the technologies described above; The present invention provides a kind of direct-acting overflow valve; The spring that comprises valve body with filler opening and return opening, spool and this spool is biased into the normality sealing station; Said spool has the oil-feed pressure-bearing surface; The hydraulic oil of said filler opening input can act on this oil-feed pressure-bearing surface and to realize overflow to promote resistance that spool overcomes spring to move; Wherein, The hydraulic oil reaction chamber that said direct-acting overflow valve also comprises remote control port and is communicated with this remote control port, this hydraulic oil reaction chamber is communicated with filler opening, and the hydraulic oil in the said hydraulic oil reaction chamber is identical with the force direction of said spring to the force direction of this spool; And the hydraulic oil effective active area of said oil-feed pressure-bearing surface is greater than the hydraulic oil effective active area of the compression face that is exposed to hydraulic oil reaction chamber of said spool, so that the active force that the active force that the driving spool that the hydraulic oil of identical oil pressure forms said oil-feed pressure-bearing surface moves moves greater than the prevention spool that said compression face is formed.
In order to realize big flow off-load; The small flow overflow; Preferably; The outer circumferential face of said spool is sliding combined with piston, and the inner peripheral surface of the valve pocket of the outer circumferential face of this piston and said valve body is slidingly matched, and an end end face of said piston is exposed to said hydraulic oil reaction chamber; The first ladder stop surface that the other end is formed on towards protrusion on the valve pocket inwall of said valve body is formed on the second ladder stop surface on the said spool outer circumferential face with protrusion; Can contacting with the second ladder stop surface with this first ladder stop surface, when said spool was in said normality sealing station, the distance between the other end of said first ladder stop surface and said spool was less than the distance between the other end of the said second ladder stop surface and this spool.
Preferably, the said hydraulic oil reaction of the spring chamber double as chamber of said direct-acting overflow valve.
Typically, said filler opening and said spring chamber lay respectively at the opposite end of said spool, and the oil-feed pressure-bearing surface of said spool is exposed in the said filler opening.
Particularly; One end of said spool extend in the said spring chamber; The end that extend into said spring chamber of this spool is formed with spring seat location ladder surface and first spring seat is installed, and this first spring seat is orientated as through said spring seat location ladder surface and made the end face space that is exposed to said spring chamber towards said piston end face and said piston of this first spring seat.
Particularly, second spring seat relative with said first spring seat is installed also in the said spring chamber, an end in contact of this second spring seat and screw press, this screw press screw thread is installed in the plug that is used to seal said spring chamber.
More specifically, said spring comprises first spring and is positioned at this first spring inner and second spring coaxial with this first spring that the two ends of the two ends of this first spring and second spring are set to respectively on said first spring seat and second spring seat.
Selectively; Said spring comprises first spring and second spring; The two ends of said first spring are set to respectively on said first spring seat and second spring seat; Said second spring is supported between the end face and the supporting lip on the said spool of said spring chamber dorsad of said piston, and said first spring seat is threaded onto on the said spool, to make this second spring form pretightening force via said second spring of said Piston Compression.
Preferably; Be formed with the ring week stop lug of in said spring chamber, stretching out on the said plug; This encircles the fringe region of all stop lug corresponding to said piston end surface, contacts when said spring chamber moves to the precalculated position, to encircle all stop lug with this at this piston.
Preferably, said hydraulic oil reaction chamber is communicated with said filler opening through the damping hole that is formed on the said spool.
Particularly, on the said valve body valve pocket is installed, said hydraulic control interruption-forming and is communicated with said hydraulic oil reaction chamber through the inside oil duct that is formed on this valve pocket and the valve body on said valve pocket.
On the basis of the technological scheme of above-mentioned direct-acting overflow valve; The present invention also provides a kind of direct-acting overflow valve valve group; Comprise direct-acting overflow valve; Wherein, said direct-acting overflow valve is the described direct-acting overflow valve of above-mentioned arbitrary technological scheme, and the remote control port of this direct-acting overflow valve is connected in the return opening or the fuel tank of this direct-acting overflow valve via on-off control valve.
Specifically selectively, said on-off control valve is the bi-bit bi-pass solenoid directional control valve.
In addition, the present invention also provides a kind of hydraulic pressure skimmer circuit, and wherein, this hydraulic pressure skimmer circuit comprises above-mentioned direct-acting overflow valve valve group, and the filler opening of said direct-acting overflow valve is communicated with the working connection of hydraulic system or working oil path, and return opening is communicated with fuel tank.
Pass through technique scheme; Direct-acting overflow valve of the present invention has increased hydraulic oil reaction chamber and remote control port; And through making the hydraulic oil effective active area of oil-feed pressure-bearing surface be exposed to the hydraulic oil effective active area of the compression face in the said hydraulic oil reaction chamber greater than this spool, thereby guaranteed the realization of relief function, optionally make hydraulic oil reaction chamber draining decompression through remote control port simultaneously; Can make direct-acting overflow valve realize unloading function effectively; Simultaneously, because hydraulic oil reaction chamber is identical with the force direction of spring to the force direction of spool, therefore direct-acting overflow valve of the present invention can be selected the less spring of elasticity coefficient for use; Make that the overall operation of relief valve is comparatively light, and kept that direct-acting overflow valve is simple in structure, advantage such as responding fast, processing cost are lower.In addition; In further preferred implementation; The present invention is through the cooperation of piston, the first ladder stop surface and the second ladder stop surface; Do the time spent in realization overflow effect and off-load effectively, make valve core opening vary in size, thereby realized the function of " small flow overflow, big flow off-load ".
Other features and advantages of the present invention will partly specify in embodiment subsequently.
Description of drawings
Attached drawings is used to provide further understanding of the present invention, and constitutes the part of specification, and it is used to explain the present invention with following embodiment, but protection scope of the present invention is not limited to following accompanying drawing and embodiment.In the accompanying drawings:
Fig. 1 is the sectional structure schematic representation of the pilot operated compound relief valve of typical band remote control port in the existing technology.
Fig. 2 is the sectional structure schematic representation that disclosed differential pressure type directly moves relief valve among the Chinese utility application CN2086355U.
Fig. 3 is the hydraulic schematic diagram of the direct-acting overflow valve of the specific embodiment of the invention, and wherein the remote control port of this direct-acting overflow valve is connected with the bi-bit bi-pass solenoid directional control valve.
Fig. 4 is the sectional structure schematic representation of the direct-acting overflow valve of the specific embodiment of the invention, the wherein said direct-acting overflow valve rest position that is in the normal state.
Fig. 5 is the sectional structure schematic representation of the direct-acting overflow valve of the specific embodiment of the invention, and wherein said direct-acting overflow valve is in overflow position.
Fig. 6 is the sectional structure schematic representation of the direct-acting overflow valve of the specific embodiment of the invention, and wherein said direct-acting overflow valve is in unloading condition.
Fig. 7 is the sectional structure schematic representation of the direct-acting overflow valve of a kind of modification mode of execution of the present invention.
Fig. 8 is the sectional structure schematic representation of the direct-acting overflow valve of the another kind of modification mode of execution of the present invention.
Description of reference numerals:
1 direct-acting overflow valve; 2 bi-bit bi-pass solenoid directional control valves;
101 valve bodies; 102 spools;
103 pistons; 104 valve pockets;
105 plugs; 106 screw press;
107 locknuts; 108 first spring seats;
109 first springs; 110 second springs;
111 second spring seats; 112 first ladder stop surfaces;
113 second ladder stop surfaces; The all stop lug of 114 rings;
115 supporting lips; X hydraulic oil reaction chamber;
The Y spring chamber; The P filler opening;
PA oil-feed pressure-bearing surface; The T return opening;
The V remote control port.
Embodiment
Be elaborated below in conjunction with the accompanying drawing specific embodiments of the invention, should be understood that, embodiment described herein only is used for explanation and explains the present invention, and protection scope of the present invention is not limited to following embodiment.
Fig. 3 to Fig. 6 shows a kind of embodiment of direct-acting overflow valve of the present invention; The formula that needs explanation; Fig. 3 is to the preferred structure that is merely direct-acting overflow valve of the present invention shown in Figure 6, the detail that the technical conceive of direct-acting overflow valve of the present invention is not limited to show among the figure.In addition, in the explanation hereinafter, except that specifying connected relation, corresponding chambers should keep sealing or basic sealing, to avoid existing the oily phenomenon of string.
With reference to Fig. 3 to Fig. 6; Spool 102 in the valve pocket that direct-acting overflow valve of the present invention comprises valve body 101 with oil inlet P and oil return inlet T, be slidingly fitted in this valve body 101 and the spring that this spool 102 is biased into the normality sealing station; Spool 102 has oil-feed pressure-bearing surface PA; It should be noted that at this this oil-feed pressure-bearing surface PA directly can directly be exposed in the oil inlet P in oil inlet P when an end of spool 102 forms, but to those skilled in the art apparently; Oil inlet P also can be communicated to the oil suction chamber of spool 102 1 ends through inner oil-feed oil duct, and this moment, the oil-feed pressure-bearing surface PA of spool 102 then was exposed in the oil suction chamber.For relief valve; The hydraulic oil of oil inlet P input can act on when reaching the cracking pressure of relief valve on this oil-feed pressure-bearing surface PA, moves and realizes overflow thereby promote resistance that spool 102 overcomes spring, wherein; Direct-acting overflow valve of the present invention also comprises remote control port V and the hydraulic oil reaction chamber X that is communicated with this remote control port V; The spring chamber Y double as hydraulic oil reaction chamber X of relief valve in Fig. 4, but to those skilled in the art apparently, through simple malformation; Hydraulic oil reaction chamber also can independently form, and is not limited to the details of Fig. 4.
As shown in Figure 4; The spring chamber Y of double as hydraulic oil reaction chamber X is communicated with said oil inlet P; Typically be communicated with through the damping hole that axially is formed on the spool 102, can certainly be communicated with through the inside oil duct that is formed on the valve body 101, hydraulic oil reaction chamber X is generally less relatively with the cross-sectional flow area that is communicated with oil duct of oil inlet P; This mainly is can release the hydraulic oil in the hydraulic oil reaction chamber rapidly through remote control port V when considering off-load, guarantees rapid off-load.
Hydraulic oil in the said hydraulic oil reaction chamber X is identical with the force direction of said spring to the force direction of spool 102, and said oil-feed pressure-bearing surface PA " hydraulic oil effective active area " is greater than " the hydraulic oil effective active area " of the compression face of the said hydraulic oil reaction chamber X of being exposed to of said spool 102.Need to prove at this; As mentioned above; Hydraulic oil reaction chamber X is not limited to the structural type of the spring chamber Y double as hydraulic oil reaction chamber X shown in Fig. 4; In technical conceive scope of the present invention, hydraulic oil reaction chamber X can form separate chamber, under this situation; Spool 102 exposes the anti-compression face of doing in the X of chamber of hydraulic oil and can exist a plurality ofly, thereby the hydraulic oil in the said hydraulic oil reaction chamber X generally can be hydraulic oil to the active force of each compression face to the active force of spool 102 effect on spool movement direction (be spool axially) is made a concerted effort.In addition, the oil-feed pressure-bearing surface PA at oil inlet P place also is not limited to form the situation of single oil-feed pressure-bearing surface PA.
In general; The no matter quantity or the shape of the compression face that is exposed to hydraulic oil reaction chamber X of the oil-feed pressure-bearing surface PA of spool 102 and spool 102; As long as the active force that the active force that the driving spool 102 that makes the hydraulic oil active area of the compression face that is exposed to hydraulic oil reaction chamber X of hydraulic oil active area and spool 102 of oil-feed pressure-bearing surface PA of spool 102 form to make the hydraulic oil of identical oil pressure that oil-feed pressure-bearing surface PA is formed moves moves greater than the prevention spool 102 that said compression face is formed; That is to say; As long as make the hydraulic oil effective active area of said oil-feed pressure-bearing surface PA greater than the hydraulic oil effective active area of the compression face of the said hydraulic oil reaction chamber X of being exposed to of said spool 102, promptly can realize the correlation of above-mentioned active force.Particularly; Because the hydraulic oil acting surface on the spool 102 might not be perpendicular to the movement direction of spool 102; Just there is the situation of the conical surface in oil-feed pressure-bearing surface PA for example shown in Figure 4; And in some hydraulic fluid ports or oil pocket, there is the problem that also exists active force to cancel out each other under the situation of a plurality of hydraulic oil acting surfaces; Therefore in the hydraulic efficiency slide valve field; Those skilled in the art represent the corresponding hydraulic fluid port of spool or the area relationship between the hydraulic oil acting surface in the oil pocket through the term of " hydraulic oil effective active area " usually; Its concrete implication is following: the hydraulic oil of a certain oil pressure acts on each hydraulic oil acting surface of a certain oil pocket of being exposed to of spool or hydraulic fluid port; Thereby be formed for driving the active force that spool moved or stoped a certain numerical value that spool moves (under the situation that has a plurality of hydraulic oil acting surfaces, refer to overall effect make a concerted effort); Then the active force of this numerical value promptly is " a hydraulic oil effective active area " divided by the oil pressure of above-mentioned hydraulic oil; This " hydraulic oil effective active area " comes from oil pressure and multiply by the well-known formula that active area equals hydraulic action; Under the situation that the spool movement direction has been confirmed, each hydraulic oil acting surface that is exposed to a certain oil pocket or hydraulic fluid port of spool need be converted into along spool movement direction area of contour on perpendicular to the plane of spool movement direction and calculate, and the area of contour of each hydraulic oil acting surface needs exist according to the force direction that bears and offsets or the problem of addition; Therefore " hydraulic oil effective active area " can project on the plane perpendicular to the spool movement direction along the spool movement direction through each hydraulic oil acting surface with a certain oil pocket of being exposed to of spool or hydraulic fluid port; And and then according to the receiving force direction to carry out the addition of area of contour or offset to calculate obtain of each hydraulic oil acting surface, but and the real area with the hydraulic oil acting surface is consistent scarcely, for example oil-feed pressure-bearing surface PA comprises the situation of the conical surface among Fig. 4.Who knowledge the conversion of the hydraulic oil effective active area of relevant valve core of the spool valve in each hydraulic fluid port or oil pocket is to those skilled in the art, repeats no more at this.
In above-mentioned embodiment; Direct-acting overflow valve of the present invention has increased hydraulic oil reaction chamber and remote control port V; And through making the hydraulic oil effective active area of oil-feed pressure-bearing surface PA be exposed to the hydraulic oil effective active area of the compression face in the said hydraulic oil reaction chamber X greater than spool 102; When the oil inlet P oil-feed; When the hydraulic fluid pressure of oil inlet P arrives predetermined value, although the oil pressure in the hydraulic oil reaction this moment chamber X is identical with the oil pressure at oil inlet P place, because the area of oil-feed pressure-bearing surface PA is exposed to the hydraulic oil active area in the said hydraulic oil reaction chamber X greater than spool 102; Correspondingly the hydraulic oil at oil inlet P place to the thrust of spool 102 greater than the thrust of the hydraulic oil in the hydraulic oil reaction chamber X to spool 102; In a single day the difference of both thrust greater than the pretightening force of spring, just can promote spool 102 and leave the normality sealing station, and the volume of hydraulic oil reaction this moment chamber X diminishes; Oil pressure in the hydraulic oil reaction chamber X increases rapidly; Make the hydraulic oil in the hydraulic oil reaction chamber X to be back to oil inlet P, thereby guaranteed the realization of relief function, optionally make hydraulic oil reaction chamber draining X decompression through remote control port V simultaneously through the circulation oil duct (for example damping hole) between oil inlet P and the hydraulic oil reaction chamber X; Can make direct-acting overflow valve realize unloading function effectively; In addition, because hydraulic oil reaction chamber is identical with the force direction of spring to the force direction of spool, therefore direct-acting overflow valve of the present invention can be selected the less spring of elasticity coefficient for use; Make that the overall operation of relief valve is comparatively light, and kept that direct-acting overflow valve is simple in structure, advantage such as responding fast, processing cost are lower.
In order to realize the function of big flow off-load, small flow overflow; Referring to Fig. 4 and shown in Figure 6; It (generally can be the Spielpassung that can form slide relative that the outer circumferential face of said spool 102 is sliding combined with piston 103; And keep sealing); And it (generally can be the Spielpassung that can form slide relative that the inner peripheral surface of the valve pocket of the outer circumferential face of this piston 103 and valve body 101 is slidingly matched; And keep sealing); One end end face of piston 103 is exposed to said hydraulic oil reaction chamber X (the for example spring chamber Y among Fig. 4), and the first ladder stop surface 112 that the other end is formed on towards protrusion on the valve pocket inwall of valve body 101 is formed on the second ladder stop surface 113 on said spool 102 outer circumferential faces with protrusion, with (the hydraulic oil reaction chamber X dorsad in the other end of piston 103 this piston during by the promotion of the hydraulic fluid pressure in the hydraulic oil reaction chamber X; Spring chamber Y for example) contacts with this first ladder stop surface 112; And make this second ladder stop surface (113) contact with the other end of this piston at spool 102 during by the hydraulic oil pressure force urges of oil inlet P, when said spool was in said normality sealing station, the distance between the other end of said first ladder stop surface 112 and said spool 102 was less than the distance between the other end of the said second ladder stop surface 113 and this spool 102.
Referring to Fig. 4, typically, said oil inlet P and said spring chamber Y lay respectively at the opposite end of spool 102, and the oil-feed pressure-bearing surface PA of said spool 102 is exposed in the said oil inlet P.Under the situation of spring chamber Y double as hydraulic oil reaction chamber X; One end of spool 102 extend in the spring chamber Y; The end that extend into spring chamber Y of this spool 102 is formed with spring seat location ladder surface and first spring seat 108 is installed; This first spring seat 108 through said spring seat location ladder surface orientate as make this first spring seat 108 towards the end face space that is exposed to spring chamber Y of end face and the piston 103 of piston 103, avoid the hydraulic oil active area of first spring seat increase spool in spring chamber when this is main.Also be equipped with in the said spring chamber Y and the second relative spring seat 111 of said first spring seat 108; One end in contact of this second spring seat 111 and screw press 106; These screw press 106 screw threads are installed in the plug 105 that is used to seal said spring chamber Y, and the other end of screw press 106 is generally fastening through locknut 107 lockings.Plug 105 generally can be installed on the valve body 101 through the outside thread of its outer circumferential face.
In direct-acting overflow valve of the present invention; Above-mentioned spring can with conventional relief valve in equally adopt a spring; But in order to make the operation of relief valve steadily reliable more, preferably, referring to shown in Figure 4; Said spring comprises second spring 110 that first spring 109 is inner and coaxial with this first spring 109 with being positioned at this first spring 109, and the two ends of the two ends of this first spring 109 and second spring 110 are set to respectively on first spring seat 108 and second spring seat 111.
A kind of modification mode of execution as spring; Referring to shown in Figure 7; Still can comprise first spring 109 and second spring 110 at spring described in this variant; Wherein only first spring (109) is arranged in the spring chamber Y, and the two ends of this first spring are set to respectively on first spring seat 108 and second spring seat 111, and second spring 110 is supported between the end face and the supporting lip 115 on the spool 102 of the Y of spring chamber dorsad of piston 103; First spring seat 108 is threaded onto on the spool 102, to make this second spring 110 form pretightening force via said piston 103 compression second springs 110.
On the basis of above-mentioned mode of execution; In order to form spacing to piston 103 during in off-load at direct-acting overflow valve of the present invention; As a kind of optimal way; Referring to shown in Figure 8, be formed with the ring week stop lug 114 of in said spring chamber Y, stretching out on the said plug 105, this encircles the fringe region of all stop lug 114 corresponding to piston 103 end faces; Contact when said spring chamber Y moves to the precalculated position, to encircle all stop lug 114, thereby the motion of piston 103 is formed position-limiting action with this at this piston 103.
In addition, referring to shown in Figure 4, particularly, on the said valve body 101 valve pocket 104 is installed, said hydraulic control mouth V-arrangement becomes on valve pocket 104, and is communicated with hydraulic oil reaction chamber X through the inside oil duct that is formed on this valve pocket 104 and the valve body 101.
On the basis of the technological scheme of above-mentioned direct-acting overflow valve; Referring to Fig. 3; The present invention also provides a kind of direct-acting overflow valve valve group, comprises direct-acting overflow valve, wherein; Said direct-acting overflow valve is the described direct-acting overflow valve of technique scheme, and the remote control port V of this direct-acting overflow valve is connected in the oil return inlet T or the fuel tank of this direct-acting overflow valve via on-off control valve.Typically; On-off control valve is a bi-bit bi-pass solenoid directional control valve 2; Certainly to those skilled in the art; On-off control valve can also adopt the control valve of other type, and for example bi-bit bi-pass hand-operated direction valve, switch valve etc. are as long as can realize the oil return inlet T of remote control port V and direct-acting overflow valve or the break-make of the oil circuit between the fuel tank.
In addition, the present invention also provides a kind of hydraulic pressure skimmer circuit, and wherein, this hydraulic pressure skimmer circuit comprises above-mentioned direct-acting overflow valve valve group, and the filler opening T of said direct-acting overflow valve is communicated with the working connection or the working oil path of hydraulic system, and oil return inlet T is communicated with fuel tank.
Followingly describe the working principle of direct-acting overflow valve of the present invention to preferred implementation shown in Figure 8, it should be noted that protection scope of the present invention is not limited to Fig. 3 to detail shown in Figure 8 with reference to Fig. 3.
Referring to shown in Figure 3, the remote control port V of direct-acting overflow valve of the present invention is connected with a bi-bit bi-pass solenoid directional control valve, and it mainly acts on is that control remote control port V is communicated with fuel tank or blocks, so that spring chamber Y release or the pressurize of double as hydraulic oil reaction chamber X.
Referring to shown in Figure 4; When relief valve is not worked or the oil pressure of oil inlet P when being lower than setting pressure; First spring seat 108 is against on the spool 102; Because the conical surface of the effect spool 102 of spring force contacts with the seamed edge of valve body 101 inner chambers, thereby form linear sealing, make oil inlet P cut off mutually with the oil return inlet T mouth.In order to guarantee that spring force can act on the spool 102 fully, remain with certain free gap between the piston 103 and first spring seat 108, this spring seat location ladder surface that extend on the end in the spring chamber Y through spool 102 is realized.The inner peripheral surface of the outer circumferential face of spool 102 and piston 103 forms the Spielpassung that can slide and seal, and one section inner peripheral surface of the valve pocket of the outer circumferential face of piston 103 and valve body 101 forms the Spielpassung that can slide and seal.The main effect of this two places Spielpassung is to guarantee again when spring chamber Y is cut off with the oil return inlet T mouth mutually that piston 103 and spool 102 can move.Having damping hole on the spool 102 makes oil inlet P be connected with spring chamber Y.In addition, the spring chamber Y of double as hydraulic oil reaction chamber X is connected with remote control port V.
Its working principle is following:
The first, relief function: like Fig. 3 and shown in Figure 5.Oil inlet P oil-feed, and bi-bit bi-pass solenoid directional control valve 2 dead electricity.Because bi-bit bi-pass solenoid directional control valve 2 dead electricity, so remote control port V is different with fuel tank, the hydraulic fluid pressure in the spring chamber Y is able to keep, and then when the oil inlet P oil-feed, the oil pressure of oil inlet P equates with the oil pressure of spring chamber Y.In this state; The hydraulic oil of oil inlet P to the active force of spool 102 to the right; In embodiment shown in Figure 4, the hydraulic oil effective active area of the oil-feed pressure-bearing surface PA of spool 102 is the sectional area that the sectional area of oil inlet P deducts the damping hole in the spool 102; The hydraulic oil of spring chamber Y can be to spool 102 generations active force left simultaneously; The hydraulic oil effective active area of the compression face that is exposed to this spring chamber of spool 102 is that the section area that the sectional area (equating with the sectional area of the endoporus of piston 103) of the spool part that piston 103 is installed of spool 102 deducts spool 102 internal damping holes (is annotated: owing to having the gap between the piston 103 and first spring seat 108; Therefore the pressure that bears on first spring seat 108 can be cancelled out each other, and deducts the sectional area of the damping hole in the spool 102 thereby the hydraulic oil effective active area is the sectional area of the spool part that piston 103 is installed of spool).Because the sectional area of oil inlet P is greater than the sectional area of the spool part that piston 103 is installed of spool; Also that is to say; The hydraulic oil effective active area of the oil-feed pressure-bearing surface PA correspondence of spool is greater than the hydraulic oil effective active area that is exposed to the compression face in the spring chamber Y (this spring chamber Y double as hydraulic oil reaction chamber X in illustrated optimal way) of spool 102; Therefore above-mentioned two power make a concerted effort be level to the right, and increase along with the increase of oil inlet P oil pressure.When the oil pressure of oil inlet P increases to a certain degree, will overcome spring force to the active force of spool 102 and promote spool 102 and move right.Because piston 103 also receives the active force left of spring chamber Y, thereby the left side of piston 103 is against on the first ladder stop surface 112 of valve body 101.So when relief valve during in overflow the stroke of spool 102 can be limited by piston, aperture efficiency is less, thereby realizes the overflow of small flow.
The second, unloading function: like Fig. 3 and shown in Figure 6, the oil inlet P oil-feed, bi-bit bi-pass solenoid directional control valve 2.At this moment, because bi-bit bi-pass solenoid directional control valve 2 must be electric, then remote control port V communicates with oil return T, so spring chamber Y decompression.So, when the oil inlet P oil-feed, the active force that hydraulic oil produces to the right spool 102, the active force that first spring 109 and 110 pairs of spools of second spring 102 produce left.Because the hydraulic oil effective active area of the oil-feed pressure-bearing surface PA of oil inlet P place spool is bigger; And spring force a little less than; So under the lower situation of oil inlet P pressure, just can overcome spring force promotion spool 102 moves right; Spool 102 also can drive piston 103 through the second ladder stop surface 113 on the spool 102 and move right, and the opening of spool 102 can be relatively large like this, realized big flow off-load.When spool 102 reaches balance, the pressure of oil inlet P and spring force balance.Through design to spring, can be so that oil inlet P be only kept lower pressure.That is to say, when remote control port V is communicated with fuel tank and during release, this direct-acting overflow valve can make the working oil path off-load, promptly only has on the working oil path by spring to form lower back pressure, is not enough to overcome load.
In addition, as stated, the present invention is not limited to Fig. 3 to embodiment shown in Figure 6, for example, referring to Fig. 7, also can realize identical function through the mounting point that changes second spring 110.In this replacement scheme, changed the mounting point of second spring 110.First spring seat 108 and spool 102 can remain precompressed preferably through being threaded when making second spring 110 between spool 102 and piston 103.When bi-bit bi-pass solenoid directional control valve 2 dead electricity; Remote control port V pressurize; During the oil inlet P oil-feed, spring chamber Y pressure is identical with oil inlet P pressure, as stated; Because the hydraulic oil effective active area of the oil-feed pressure-bearing surface PA of oil inlet P place spool is greater than the hydraulic oil effective active area that is exposed to the compression face in the spring chamber Y of spool 102, making a concerted effort of these two power is active force to the right.At this moment; Piston 103 (is made also that thus the piston 103 and first spring seat 109 are spaced apart) by the pressure effect pushing and pressing that the hydraulic oil of the spring chamber Y of double as hydraulic oil reaction chamber X produces on valve body 101, then the active force of 110 pairs of spools 102 of second spring is axial forces left.When the hydraulic oil at oil inlet P place acts on active force on the oil-feed pressure-bearing surface PA greater than the hydraulic oil in first spring 109, second spring 110 and the spring chamber Y during to the making a concerted effort of spool active force, spool is opened, the relief valve overflow.When solenoid valve get electric, remote control port V decompression, during the oil inlet P oil-feed, spool 102, piston 103, second spring 110 and first spring seat 108 overcome the spring force of spring I 109 under the effect of the hydraulic oil of oil inlet P, realize the off-load effect.In this replacement scheme, second spring 110 is compressed all the time, and the precompression of second spring 110 then is the minimum set pressure of this relief valve when overflow.And the oil pressure relief minimum of relief valve can transfer to zero in technological scheme shown in Figure 4, and promptly spring does not have precompressed, under this situation, just can not realize the overflow effect certainly yet.
In addition, the structure that has an externally threaded plug 105 through change also can realize identical function.In this replacement scheme, changed the structure of plug 105.When off-load, all stop lug 114 of the ring that in said spring chamber Y, stretches out of plug 105 can limit the stroke of piston 103, thus the opening of restriction spool 102.
Can find out by last description; The invention has the advantages that: direct-acting overflow valve of the present invention has increased hydraulic oil reaction chamber X (the for example spring chamber Y of double as hydraulic oil reaction chamber X among Fig. 4) and remote control port V; And through making the hydraulic oil effective active area of oil-feed pressure-bearing surface PA be exposed to the hydraulic oil active area in the said hydraulic oil reaction chamber X greater than this spool; Thereby guaranteed the realization of relief function; Optionally make through remote control port V simultaneously and hydraulic oil reaction chamber X draining decompression can make direct-acting overflow valve realize unloading function effectively, simultaneously; Because hydraulic oil reaction chamber X is identical with the force direction of spring to the force direction of spool 102; Therefore direct-acting overflow valve of the present invention can be selected the less spring of elasticity coefficient for use, makes that the overall operation of relief valve is comparatively light, and kept that direct-acting overflow valve is simple in structure, advantage such as responding fast, processing cost are lower.In addition; In further preferred implementation; The present invention is through the cooperation of piston 103, the first ladder stop surface 112 and the second ladder stop surface 113; Do the time spent in realization overflow effect and off-load effectively, make valve core opening vary in size, thereby realized the function of " small flow overflow, big flow off-load ".That is to say; The present invention has been through having increased remote control port on direct-acting overflow valve, and through making the hydraulic oil effective active area of oil-feed pressure-bearing surface PA of spool at oil inlet P place be exposed to the hydraulic oil active area in the said hydraulic oil reaction chamber X greater than this spool, thereby make direct-acting overflow valve also have unloading function; And preferably do the time spent in realization overflow effect and off-load; Valve core opening varies in size, and has realized the function of " the big flow off-load of small flow overflow ", and it is compared with traditional direct-acting overflow valve; It can realize unloading function effectively through remote control port; Compare with the pilot operated compound relief valve of traditional band remote control, it is simple in structure, is easier to installation and maintenance.Therefore, direct-acting overflow valve of the present invention has the advantage of direct-acting overflow valve and pilot operated compound relief valve concurrently
More than combine accompanying drawing to describe preferred implementation of the present invention 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 that in addition each the concrete technical characteristics described in above-mentioned embodiment under reconcilable situation, can make up through 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 regarded as the disclosed content of the present invention equally.
Claims (14)
1. direct-acting overflow valve; The spring that comprises the valve body (101), spool (102) of have filler opening (P) and return opening (T) and this spool (102) is biased into the normality sealing station; Said spool (102) has oil-feed pressure-bearing surface (PA); The hydraulic oil of said filler opening (P) input can act on this oil-feed pressure-bearing surface (PA) and go up to promote resistance that spool (102) overcomes spring and move and realize overflow, wherein
Said direct-acting overflow valve also comprises remote control port (V) and the hydraulic oil reaction chamber (X) that is communicated with this remote control port (V); This hydraulic oil reaction chamber (X) is communicated with filler opening (P); Hydraulic oil in the said hydraulic oil reaction chamber (X) is identical with the force direction of said spring to the force direction of this spool (102); And the hydraulic oil effective active area of said oil-feed pressure-bearing surface (PA) is greater than the hydraulic oil effective active area of the compression face that is exposed to hydraulic oil reaction chamber (X) of said spool (102), so that the active force that the active force that the driving spool (102) that the hydraulic oil of identical oil pressure forms said oil-feed pressure-bearing surface (PA) moves moves greater than the prevention spool (102) that said compression face is formed.
2. direct-acting overflow valve according to claim 1; Wherein, The outer circumferential face of said spool (102) is sliding combined with piston (103); And the inner peripheral surface of the valve pocket of outer circumferential face of this piston (103) and said valve body (101) is slidingly matched; One end end face of said piston (103) is exposed to said hydraulic oil reaction chamber (X); The first ladder stop surface (112) and protrusion that the other end is formed on towards protrusion on the valve pocket inwall of said valve body (101) are formed on the second ladder stop surface (113) on said spool (102) outer circumferential face; Can contacting with the second ladder stop surface (113) with this first ladder stop surface (112), when said spool was in said normality sealing station, the distance between the other end of said first ladder stop surface (112) and said spool (102) was less than the distance between the other end of the said second ladder stop surface (113) and this spool (102).
3. direct-acting overflow valve according to claim 2, wherein, the spring chamber of said direct-acting overflow valve (Y) double as said hydraulic oil reaction chamber (X).
4. direct-acting overflow valve according to claim 3; Wherein, Said filler opening (P) and said spring chamber (Y) lay respectively at the opposite end of said spool (102), and the oil-feed pressure-bearing surface (PA) of said spool (102) is exposed in the said filler opening (P).
5. direct-acting overflow valve according to claim 3; Wherein, One end of said spool (102) extend in the said spring chamber (Y); The end that extend into said spring chamber (Y) of this spool (102) is formed with spring seat location ladder surface and first spring seat (108) is installed, and this first spring seat (108) is orientated as through said spring seat location ladder surface and made the end face space that is exposed to said spring chamber (Y) towards the end face and the said piston (103) of said piston (103) of this first spring seat (108).
6. direct-acting overflow valve according to claim 5; Wherein, Second spring seat (111) relative with said first spring seat (108) also is installed in the said spring chamber (Y); One end in contact of this second spring seat (111) and screw press (106), this screw press (106) screw thread is installed in the plug (105) that is used to seal said spring chamber (Y).
7. direct-acting overflow valve according to claim 6; Wherein, Said spring comprises first spring (109) and is positioned at inner and second spring (110) coaxial with this first spring (109) of this first spring (109) that the two ends of the two ends of this first spring (109) and second spring (110) are set to respectively on said first spring seat (108) and second spring seat (111).
8. direct-acting overflow valve according to claim 6; Wherein, Said spring comprises first spring (109) and second spring (110); The two ends of said first spring (109) are set to respectively on said first spring seat (108) and second spring seat (111); Said second spring (110) is supported between the end face and the supporting lip (115) on the said spool (102) of said dorsad spring chamber (Y) of said piston (103), and said first spring seat (108) is threaded onto on the said spool (102), with via said piston (103) compression said second spring (110) and make this second spring (110) form pretightening force.
9. direct-acting overflow valve according to claim 6; Wherein, Be formed with the ring week stop lug (114) of in said spring chamber (Y), stretching out on the said plug (105); This encircles the fringe region of all stop lug (114) corresponding to said piston (103) end face, contacts to encircle all stop lug (114) with this towards said spring chamber (Y) when moving to the precalculated position at this piston (103).
10. according to each described direct-acting overflow valve in the claim 1 to 9, wherein, said hydraulic oil reaction chamber (X) is communicated with said filler opening (P) through the damping hole that is formed on the said spool (102).
11. direct-acting overflow valve according to claim 10; Wherein, Valve pocket (104) is installed on the said valve body (101); Said hydraulic control mouth (V) is formed on the said valve pocket (104), and is communicated with said hydraulic oil reaction chamber (X) through the inside oil duct that is formed on this valve pocket (104) and the valve body (101).
12. direct-acting overflow valve valve group; Comprise direct-acting overflow valve; Wherein, Said direct-acting overflow valve is according to each described direct-acting overflow valve in the claim 1 to 11, and the remote control port of this direct-acting overflow valve (V) is connected in the return opening (T) or the fuel tank of this direct-acting overflow valve via on-off control valve.
13. direct-acting overflow valve valve group according to claim 12, wherein, said on-off control valve is bi-bit bi-pass solenoid directional control valve (2).
14. hydraulic pressure skimmer circuit; Wherein, This hydraulic pressure skimmer circuit comprises that the filler opening of said direct-acting overflow valve (T) is communicated with the working connection or the working oil path of hydraulic system according to claim 12 or 13 described direct-acting overflow valve valve groups, and return opening (T) is communicated with fuel tank.
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| CN201210175068.4A CN102678645B (en) | 2012-05-31 | 2012-05-31 | Direct-acting overflow valve, direct-acting overflow valve group and hydraulic overflow loop |
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| CN102678645B CN102678645B (en) | 2014-10-29 |
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| CN103016432A (en) * | 2012-12-17 | 2013-04-03 | 三一重工股份有限公司 | Secondary relief valve, hydraulic lowering system for cranes and crane |
| CN103644339A (en) * | 2013-11-25 | 2014-03-19 | 大连元利流体技术有限公司 | Pollution resistant pilot operated relief valve |
| CN103758807A (en) * | 2014-01-10 | 2014-04-30 | 张思学 | Automobile differential constant-current steering booster pump or threaded differential relief cartridge valve |
| CN105587700A (en) * | 2014-10-20 | 2016-05-18 | 卡特彼勒公司 | Hydraulic valve device, hydraulic system containing same and robot containing hydraulic system |
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| CN106438549A (en) * | 2016-12-08 | 2017-02-22 | 燕山大学 | Direct-acting overflow valve |
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| CN103016432B (en) * | 2012-12-17 | 2016-02-10 | 三一重工股份有限公司 | Secondary relief, hoist fall width hydraulic system and hoist |
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| CN103758807A (en) * | 2014-01-10 | 2014-04-30 | 张思学 | Automobile differential constant-current steering booster pump or threaded differential relief cartridge valve |
| CN105587700A (en) * | 2014-10-20 | 2016-05-18 | 卡特彼勒公司 | Hydraulic valve device, hydraulic system containing same and robot containing hydraulic system |
| CN105587700B (en) * | 2014-10-20 | 2018-05-25 | 卡特彼勒公司 | Fluid pressure valve device and hydraulic system and machine including the fluid pressure valve device |
| CN105805072A (en) * | 2016-05-17 | 2016-07-27 | 山东栋梁科技设备有限公司 | Multifunctional overflow valve for teaching and practical training and operation method |
| CN106438549A (en) * | 2016-12-08 | 2017-02-22 | 燕山大学 | Direct-acting overflow valve |
| CN106438549B (en) * | 2016-12-08 | 2018-02-09 | 燕山大学 | A kind of direct-acting overflow valve |
| CN106895037B (en) * | 2017-04-20 | 2018-07-13 | 北京航空航天大学 | Permanent magnetic spring direct-acting overflow valve based on air gap combination |
| CN106895037A (en) * | 2017-04-20 | 2017-06-27 | 北京航空航天大学 | Permanent magnetic spring direct-acting overflow valve based on air gap combination |
| CN108131345A (en) * | 2017-12-21 | 2018-06-08 | 宁波文泽机电技术开发有限公司 | A kind of high-damping direct-acting overflow valve |
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| CN108506266A (en) * | 2018-07-06 | 2018-09-07 | 佛山信卓派思机械科技有限公司 | A kind of plug-in proportioning valve |
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| CN109058213B (en) * | 2018-11-05 | 2019-12-03 | 万静琼 | A kind of valve |
| CN112780623A (en) * | 2020-12-25 | 2021-05-11 | 哈尔滨工业大学 | Overflow valve suitable for there is back pressure operating mode compensation hydraulic power |
| CN113217497A (en) * | 2021-05-24 | 2021-08-06 | 西安航天远征流体控制股份有限公司 | Plug-in type energy storage overflow valve |
| CN113217497B (en) * | 2021-05-24 | 2023-11-21 | 西安航天远征流体控制股份有限公司 | Plug-in type energy storage overflow valve |
| CN113107742A (en) * | 2021-05-28 | 2021-07-13 | 北京天地玛珂电液控制系统有限公司 | Pressure difference type outer rotor hydroelectric generator and pressure regulating system |
| CN113217254A (en) * | 2021-05-28 | 2021-08-06 | 北京天地玛珂电液控制系统有限公司 | Fluid power generation device |
| CN113685387A (en) * | 2021-07-19 | 2021-11-23 | 北京天地玛珂电液控制系统有限公司 | Pressure balance type water-based proportional reversing valve |
| CN113685387B (en) * | 2021-07-19 | 2023-10-27 | 北京天玛智控科技股份有限公司 | Pressure balance type water-based proportional reversing valve |
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