CN101305228B - Double seat valve - Google Patents

Double seat valve Download PDF

Info

Publication number
CN101305228B
CN101305228B CN2006800421894A CN200680042189A CN101305228B CN 101305228 B CN101305228 B CN 101305228B CN 2006800421894 A CN2006800421894 A CN 2006800421894A CN 200680042189 A CN200680042189 A CN 200680042189A CN 101305228 B CN101305228 B CN 101305228B
Authority
CN
China
Prior art keywords
closing component
valve seat
double seated
section
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN2006800421894A
Other languages
Chinese (zh)
Other versions
CN101305228A (en
Inventor
J·布尔梅斯特
M·聚德尔
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GEA Tuchenhagen GmbH
Original Assignee
Tuchenhagen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tuchenhagen GmbH filed Critical Tuchenhagen GmbH
Priority claimed from PCT/EP2006/001483 external-priority patent/WO2007054131A1/en
Publication of CN101305228A publication Critical patent/CN101305228A/en
Application granted granted Critical
Publication of CN101305228B publication Critical patent/CN101305228B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Abstract

The invention relates to a double seat valve, which is capable of cleaning the seat and which is improved compared to that of the prior art, whereby a delivery as free from turbulence as possible of the seat cleaning flow into and out of a leakage cavity is ensured, and a pressure-increasing direct action upon the seat areas is reliably prevented. This is achieved in that: a second closing element (4), when in its closed position, rests with a stopping surface (4e), which is placed on an end face of its cylindrical projection (4*), upon a transition interface (2e, 2e*) and, to be precise, directly upon a first seat face (2a, 2g) in an adjoining manner; in the end face of a second cylindrical projection (4*), a central recess (4d) is provided which, radially outside, starts (a starting point of a contour (K)) with a rotationally symmetric reversing surface (4b) and is delimited on an end side by an end face (4c) oriented, in essence, essentially perpendicular to a longitudinal axis of the second closing element (4), the reversing surface (4b) leading into the end face (4c) (a leading point of the contour (K)) ; the reversing surface (4b) and the stopping surface (4e) form a second wraparound edge (U2) that, when the second closing element (4) is closed, directly abuts against a first end section (2g) of the first seat face (2a); when viewing a meridian section, the reversing surface (4b) has the contour (K) with a bend-free curve, a direction vector in the leading point of the reversing surface (4b) points into a discharge borehole (3d) centrally provided in a first closing element (3) without colliding with the first closing element (3) in the vicinity of its areas bordering a leakage cavity (5) or of a middle seal (8, 8*) and forming dynamic pressure, and an end side delimitation of the first closing element (3) facing the leakage cavity (5) is at an axial safe distance (x) from a direction vector on an outlet point of the transition interface (2e) into the first end section (2g).

Description

Double seated valve
Technical field
The present invention relates to a kind of double seated valve that comprises two series connection closing components that be provided with, that can move mutually.
Background technique
By the double seated valve of the known a kind of this type of DE 196 08 792 C2, owing to can allow function that the valve seat surface that exposes is respectively cleaned by open its valve seat surface with gap width, this double seated valve is also referred to as the double seated valve that can clean valve seat.In known double seated valve, each in three seal rings all relates to a kind of discrete seal ring, and wherein each seal ring has only simple function.First seal ring in first closing component is a pure radial effect seal ring, and it slides in being designed to first valve seat surface of cylindrical peripheral face and seals there owing to the bias voltage (with the seal ring of slip joint) that is provided with.At second seal ring on second closing component or affact on second valve seat surface of conical design, and be referred to as the seal ring (with the seal ring of compressive engagement) of axial/radial effect, or a pure radial effect seal ring (with the seal ring of slip joint) also is set at this.Generally, if a seal ring with compressive engagement is set, then on second valve seat surface, also there is firm (metal) backstop of the end position (closed position) that is used to limit second closing component.The 3rd seal ring also is so-called intermediate seal circle, if in opening stroke, first closing component abuts on second closing component by this intermediate seal circle, and opening in the movement process of a step, when second closing component took the position of opening fully to, the 3rd seal ring was put its function (with the seal ring of compressive engagement) to good use.At this, the intermediate seal circle is arranged on the end face in a close leakage chamber on related second closing component that drives.
More than Jian Shu known double seated valve has two so-called valve seat cleaning positions, and wherein the first valve seat cleaning position is produced by first portion's stroke reverse with opening stroke.On this position, the cylindrical projection that is arranged on first closing component in leakage chamber side forms a so-called throttle clearance with cylindrical first valve seat surface that matches, by this throttle clearance, the detergent flow that flows through from the first adjacent valve chamber can be limited.The valve seat cleaning position of second closing component be by one with open stroke second portion stroke in the same way and obtain, wherein partially opening on the position, the cylindrical projection that is arranged on second closing component in leakage chamber side partly forms one second throttle clearance with matching of open communication, and this second throttle clearance is limited in the flow of the second valve seat cleaning fluid that produces on this valve seat cleaning position.
Because two closing components have different diameters with the cylindrical projection that matches, section also has different diameters so each of open communication matches, and has just realized a transitional surface like this between these two diameters.Valve seat cleaning position at first closing component, the first valve seat cleaning fluid flows and strikes on the distolateral border on second closing component along columniform valve seat surface, wherein the diameter of two sections by open communication is poor, has prevented directly bump second throttle clearance valve seat area of clashing into second closing component then of the first valve seat cleaning fluid.At the valve seat cleaning position of second closing component, on the transitional surface of diameter difference between each section of cross-over connection open communication, the second valve seat cleaning fluid by radially to intrinsic deflection and from the top of first closing component distolateral interface next door flow through.In this case, need prevent that equally the second valve seat cleaning fluid from directly clashing into the valve seat area that first closing component is clashed in the first throttle gap then.
By known double seated valve, can be limited in the detergent consumption in the respective valve seat cleaning course on request.Yet, requirements at the higher level have been proposed this double seated valve in some country.For example in the U.S., have than the big sealing ring defective or even lose under the situation of one at two valve seat inserts, in valve seat cleaning course, require the valve seat area that does not have detergent to pass corresponding seal ring defective or do not have seal ring to another closing component.Under these condition, the requirement that this class double seated valve not only is limited by the consumption of restriction detergent in the valve seat cleaning course and avoids valve seat area is directly loaded, but also be limited by following requirement: the valve seat cleaning fluid is not entered in the leakage chamber and from that with promptly having turbulent flow at first as far as possible and be discharged to the external world, and the valve seat area of respectively closing directly is loaded by the direct impact of this valve seat cleaning fluid or with the pressure that improves.
Direct loading means by corresponding valve seat cleaning fluid vertically points to the velocity component that limits each wall of valve seat area border.That is, notice that each time directly loading all causes the kinetic energy of fluid to change into static pressure.To wall or honorable projected angle of impact that it relied on, obtain a tributary that has what is called " streamline " according to fluid, wherein this streamline is divided into two fluid.Streamline itself bumps against on the what is called " stagnation point ", so be zero in the speed of this point.The pressure increase that produces owing to the termination of speed is also referred to as " stagnation pressure (Staudruck) ".The mechanism of above-mentioned boost pressure can produce a leakage flow on corresponding throttle clearance and the valve seat insert damage ring or that fully no longer exist.
Therefore, under any circumstance, all be disadvantageous to definite direct bump that leaks the face on border, chamber by the valve seat cleaning fluid.In known double seated valve, more or less vertically strike on the distolateral interface of holding the intermediate seal circle of second closing component by the first valve seat cleaning fluid that produces with first portion's stroke lifting (Anl ü ften) first closing component.At rum point, fluid is mainly also tangent with the intermediate seal circle that stretches out from end face towards the center of leaking chamber deflection over there and fluid.In addition, also produce a kind of streamline on living rum point, its tributary towards valve seat area can produce a kind of turbulent flow and a stagnation pressure at this.
Also known double seated valves (WO 98 54 494 A1; EP 0 819 876 B1), these valves have omitted described intermediate seal circle.In double seated valve according to WO9854494A1, in opening the process of motion, first valve seat insert of the radial effect of first closing component be pushed in second closing component one columniform, with the cylinder valve seat surface groove concordant, that have same diameter of first closing component in.Second closing component lifts from its valve seat surface from first closing component subsequently, and two closing components together reach the fully open position.In this structure, the radial direction seal ring of first closing component seals in closed position, and so-called intermediate seal circle works at the extracting position (Abholstellung) and the open position subsequently of double seated valve, and wherein first valve seat insert also plays pure radial seal effect (slip joint) on these positions.Second closing component is designed to a valve seat disk, a conical section acting in conjunction of its seal ring and second valve seat surface, and it also is directed to and centering on this taper shape section.If seal ring allows, on this taper shape section, also dispose firm (metal) backstop in case of necessity, be used for second closing component being carried out end position and limit in the double seated valve closed position.
When carrying out the valve seat cleaning of first closing component, the valve seat cleaning fluid is directed to and strikes the distolateral border of cylinder shape groove along the cylindrical wall of first valve seat surface and groove subsequently, and this distolateral border is preferably perpendicular to each concordant cylndrical surface orientation.Overall, the such normal deflection of fluid is disadvantageous, because fluid is shunted and produced turbulent flow and circulate from wall in uncontrolled mode, this can form stagnation pressure.In known design, also there is shortcoming, i.e. the shape and size of the groove of the shape and size of the cylinder valve seat surface in valve chamber decision in second closing component.Therefore, for this groove that the valve seat cleaning fluid is played guiding and deflecting action, just only there is limited possibility in the design of its fluidics aspect.
In EP 0 819 876 B1, described a kind of double seated valve that cleans valve seat, wherein do not had discrete intermediate seal circle equally, and wherein in cylindrical valve seat first valve seat insert of pure radial effect have dual functions.This dual functions is, is arranged on first valve seat insert on first closing component that is designed to sliding piston and also has in cylindrical valve seat axial seal function (compressive engagement) with respect to second closing component simultaneously except the radial seal function.Opening in the process of motion when reaching a so-called extracting position and transferring to open position subsequently under same case with second closing component when first closing component, the axial seal function works.
With according to the double seated valve of DE 196 08 792 C2 and opposite according to the double seated valve of WO 98 54 494 A1, in the double seated valve according to EP 0 819 876 B1, the throttle clearance on first closing component is not arranged on leaks the chamber side, but is provided with away from leaking the chamber.With respect to above-mentioned position, be used for the cylindrical projection that the face that matches with open communication forms possible throttle clearance and be under first closing component.In this structure, in order to remove first valve seat insert of radial effect from its cylinder valve seat surface that matches with gap width, need an annular groove in this open communication, in the valve seat cleaning course that matches, first valve seat insert is pulled in this annular groove.Formed desired throttle clearance at the cylindrical projection on first closing component with the section that matches of open communication under this annular groove like this.If consider simple throttle clearance effect, it is equal away from the position of leaking the chamber that this throttle clearance is configured to one from one again in the position of leaking the chamber side, yet, this change makes when second closing component is transferred to its valve seat cleaning position, the cleaning criticality occurs for first valve seat insert in first closing component.In this case, there is such danger, be the sealing area that at least a portion second valve seat cleaning fluid can directly strike first closing component, this is preposition because of here not had, cover cylindrical projection first valve seat insert, that form throttle clearance.
The valve seat insert that has the double seated valve of dual functions in the above described manner is not no problem, because they must satisfy different requirements and their action range is not clearly limited and defines, as only having respectively radially or axial/radial or only axially the situation of the discrete seal ring of function only.Because such fact is arranged, promptly unique seal ring on the one hand pure radial effect and one more or less next-door neighbour's zone must bear axially or the sealing function of axial/radial, so these corresponding sealing areas must be close relatively, and do not make seal ring have unnecessary large scale.Under existing situation, the sealing area of pure radial effect must keep certain length in the cylinder valve seat surface till the zone of axial/radial effect clings on another closing component.The common and cylinder valve seat surface partition distance of part with above-mentioned two sealing areas of cross-over connection of bifunctional valve seat insert, produce a recess storage tank sample, dark thus between seal ring and cylinder valve seat surface, this recess provides a zone that cleaning is important.
Summary of the invention
The objective of the invention is further to improve the double seated valve of described type, guaranteeing to enter or leave the valve seat cleaning fluid that leaks the chamber does not have turbulent flow as far as possible, and avoids reliably with the pressure that improves valve seat area directly being loaded.
According to the present invention, a kind of double seated valve is proposed, comprise what two series connection were provided with, the closing component of relative movement mutually, these two closing components on the closed position of double seated valve, prevent fluid from valve chamber part to another valve chamber part overflow, these two closing components all limit a border of leaking the chamber at open position and closed position, this leakage chamber is connected with the external world of double seated valve, wherein on closed position, first closing component that is designed to sliding piston is contained in the open communication of each valve chamber part that is interconnected hermetically, and opening in the process of motion the intermediate seal circle that acts on by between each closing component at it abuts in hermetically and attaches troops to a unit on second closing component of one second valve seat surface, and further opening in the motion, second closing component is also transferred to an open position, wherein first closing component has a seal ring, and the sealing circle radially seals with respect to cylindrical first valve seat surface that is formed in the open communication; Each closing component can be transferred to a valve seat cleaning position with gap width respectively by a partial journey independently of each other, so that wash its each homocentric valve seat surface, wherein second closing component can be transferred to its corresponding valve seat cleaning position by one with the second portion stroke of opening the motion equidirectional, and first closing component can be transferred to its corresponding valve seat cleaning position by one with first portion's stroke of opening the reverse movement direction; One is arranged on cylindrical projection on each closing component forms an annular respectively with the open communication that matches throttle clearance leaking the chamber side, wherein first valve seat surface has a diameter, and this diameter is attached troops to a unit in the diameter of the annular groove of second closing component less than one in open communication; And between first valve seat surface and annular groove, also have a transitional surface, it is characterized in that:
● second closing component just is close to first valve seat surface on the stop surface on the end face that is arranged on its cylindrical projection on its closed position with reclines transitional surface;
● in the end face of the cylindrical projection of second closing component, a central recess is set, this central recess radial outside start from a rotational symmetric deflection plane and distolateral by an end face limited boundary that is substantially perpendicular to the longitudinal axis orientation of second closing component, wherein deflection plane leads to the end face of central recess;
● deflection plane and stop surface form one second around seamed edge, and this second is close to a first end section of first valve seat surface around seamed edge on the closed position of second closing component;
● from the vertical centre section, deflection plane has a profile that has no flex point curve, wherein point to a middle heart and be arranged on discharge orifice on first closing component, and in the zone in those zones on border, chamber is leaked in the qualification of first closing component, do not collide and form stagnation pressure with first closing component and intermediate seal circle at the direction vector on the outflow point of deflection plane;
● and one of first closing component near the distolateral border of leaking the chamber be designed to the direction vector that one the first exit point place around seamed edge enters the first end section of transitional surface and have an axial safe distance.
According to the present invention, second valve seat surface is perpendicular to the longitudinal axis setting of double seated valve, and second closing component has one second seal ring, and this second seal ring axially seals with compressive engagement with respect to second valve seat surface.
The present invention is based on the essential characteristic according to the known double seated valve of DE 196 08 792 C2, wherein the cylindrical projection that particularly is arranged on the corresponding closing component in leakage chamber side is used to form corresponding throttle clearance.In addition, the present invention has utilized the diameter of these cylindrical projections poor, and it allows to form a transitional surface between the section of the different-diameter of open communication, and these sections are attached troops to a unit in each cylindrical projection.The principle that realizes the intermediate seal circle that separates of described purpose is, open motion until in the open position process at so-called extracting position with what execution continued, under any circumstance all keep two closing components are sealed mutually, technological scheme wherein of the present invention be not only to determine on any in two kinds of possible configurations fully aspect the position of intermediate seal circle.Technological scheme of the present invention or allow the intermediate seal circle is configured in the end face of second closing component, or allow it is configured in the end face of first closing component as alternative.
In order to realize purpose of the present invention, first inventive concept of the present invention is, in corresponding valve seat cleaning course, will be directed to and leak the chamber and do not produce turbulent flow and obstruction as far as possible, and in an identical manner it will be discharged to the external world therefrom from the valve seat cleaning fluid that the throttle clearance that matches is discharged.Reach this purpose, this is on the one hand by a kind of flow profile new, that guide the valve seat cleaning fluid and make its deflection in leaking the chamber.The valve seat of first closing component of this new flow profile below being arranged in cleaning guarantees, the first valve seat cleaning fluid in the first valve seat surface zone along the curve of wall and not shunting (
Figure S2006800421894D00051
).Then in the central recess in an end face of a cylindrical projection that is arranged on second closing component, no ballistic throw takes place in the first valve seat cleaning fluid, such first valve seat cleaning fluid can arrive a middle heart and be arranged on discharge orifice in first closing component, and in it limits the zone of leaking the border, chamber or in the zone of intermediate seal circle, do not collide with first closing component and form stagnation pressure.This central recess is formed by a rotational symmetric deflection plane basically, it starts from the described end face of second closing component at radial outside, and distolateral by an end face limited boundary that is substantially perpendicular to the longitudinal axis orientation of second closing component, wherein this deflection plane leads to this end face.
Importantly, the no ballistic throw of valve seat cleaning fluid in deflection plane.This point is to realize like this according to the present invention, promptly from vertical centre section (Meridianschnitt), deflection plane has a profile that has no flex point curve, wherein under specified criteria, point to a middle heart and be arranged on discharge orifice in first closing component at the direction vector on the outflow point of this deflection plane, the more important thing is, form one second around seamed edge at the starting point place of this profile, this second around seamed edge at the closed position of second closing component first end section in abutting connection with first valve seat surface.
In by the water conservancy diversion process that promotes the second valve seat cleaning fluid that second closing component produces importantly, this second valve seat cleaning fluid is first shunting around the seamed edge place that a first end section by the transitional surface and first valve seat surface forms with limiting, and flows through by the face that limits the first closing component border in leaking the zone in chamber fully tangently.For this purpose, between first the possible zone around the seamed edge and first closing component safe distance is set, it can both prevent to produce relevant bump under any possible manufacturing formula skill condition.
Second basic design of the present invention is, second closing component on its closed position (is not being had the sliding piston with the seal ring of the radial effect of slip joint with the coefficient valve seat area of seal ring place, perhaps have valve seat disk in case of necessity with the seal ring of the radial/axial effect of slip/compressive engagement) carry out the end position restriction, as the common situation in known such double seated valve, but desirable with second closing component, but not to realize in all cases or firm (metal) backstop in the cards moves to the place, end away from the sealing circle of the throttle clearance that matches.According to the present invention, this point is achieved in that the stop surface that i.e. second closing component is provided with in its closed position on the end face of its cylindrical projection abuts on the transitional surface, just is close to first valve seat surface.By this measure of in known technology, not knowing, eliminated the gap in adjacency leakage chamber between second closing component and valve chamber, be usually directed to a kind of metallic seal this this.Like this, in the valve seat cleaning course of first closing component, there is not detergent can reach the second valve seat insert place that perhaps has been damaged or has perhaps lost fully by the throttle clearance that exists between cylindrical projection on second closing component and the cylinder shape groove in the valve chamber.
This type of the sealing to this important gap is still impossible so far, because will bring unnecessary qualification at the stop surface of the valve seat area of second valve seat insert.Crucially in the enforcement of the present invention second design is, second closing component and corresponding stop surface on the valve chamber can be direct, complete around and firmly contact or the Metal Contact process in can reach the degree that on the leakage chamber, seals.For this reason, all of sufficient centering guiding of second closing component that need be in valve chamber and double seated valve participate in structural members of guiding fully to neutrality.
End effect in order further to offset the wedge of second closing component in its closing movement, according to a kind of favourable structure, the end section radial outside of second cylindrical projection is right after design like this after the stop surface, thus this form an annular ring around alignment.From radial direction, this alignment position outwards move as far as possible far and as far as possible near-earth near the curve of determining by the cavetto radius of transitional surface.This by annular ring around second scarf realize, this annular ring around second scarf be arranged on the end section and extend with a relative stop surface of angle of chamfer, and second diameter with second cylindrical projection forms one the 3rd around seamed edge, the 3rd is formed by rounding around seamed edge, and has guaranteed centering on transitional surface.
According to first suggestion, the intermediate seal circle is arranged in the end face of second closing component, has wherein considered the point of deflection plane radially inner side in the end face of groove.What this valued be, at first to guarantee the deflection that is used for first valve seat cleaning of the deflection plane that at first forms by groove, and the first valve seat cleaning fluid can not run into any obstruction at intermediate seal circle place in its further curve, so just turbulent flow and shunting can be in leaking the chamber, do not formed, the local stagnation pressure that forms can be caused and form turbulent flow.Under this situation, first closing component provides a sealing surface that is used for the intermediate seal circle on the face that matches of its end section.
Another advises setting, an optional intermediate seal circle is arranged on the distolateral border of cylindrical projection of first closing component, wherein said optional intermediate seal circle preferably with the end face acting in conjunction of groove in second closing component, just with a zone of deflection plane radially inner side.Yet other point of contact also is possible, outside wherein deflection plane itself also is not precluded within.
In the variation of these two kinds of configurations, the exit point place of first closing component and deflection plane in the first end section enter into the first end section direction vector safe distance such design, make it the same big with all foozle sums of each structural member of double seated valve at least, these foozles decisions on the closed position of first closing component it to the minimum axial direction distance of transitional surface.Dispose in first closing component under the situation of optional intermediate seal circle, this safe distance should increase a distance measurements, and this intermediate seal circle stretches out this distance measurements from the distolateral border of the cylindrical projection of first closing component.
Another advises setting, and the direction vector at the starting point place of deflection plane profile is concordant with the first end section of first valve seat surface.This preferred form of implementation has been guaranteed basically that the first valve seat cleaning fluid has and has not been entered deflection plane with impacting and enter groove in second closing component then.Not only for a cylinder-shaped end section concordant, and, must guarantee above-mentioned condition for the same first end section (a so-called inclined-plane that enters) that in framework of the present invention, is provided with of a circular cone expansion with cylindrical first valve seat surface.At this, the end section of this taper shape expansion can have independent bending or crooked and outline elements straight line.
Also realized at the satisfactory result aspect the no ballistic throw according to another suggestion, departed from second angle of yaw less than 15 degree at the direction vector at the starting point place of deflection plane profile and the direction vector of first end section.The generation that the second bigger angle of yaw will cause stagnation pressure from but disadvantageous.
First of suggestion enters the inclined-plane and makes first seal ring easily enter into columniform first valve seat surface according to the present invention, and has therefore reduced the wearing and tearing of sealing circle.Yet, consider that from the fluidics aspect this enters the easier formation shortcoming in inclined-plane, because it by increasing flow cross section the sluggish first valve seat cleaning fluid, the danger of fluid shunting is arranged then.In this suggestion, make at least one circular cone outer circumferential face with forming the first first end section that enters the inclined-plane.In order not make the first valve seat cleaning fluid produce shunting on the profile of this circular cone outer circumferential face, suggestion is with this applying angle of first end section inclination, and this applying angle is preferably in 5 to the 15 degree scopes in 0 to 15 degree scope, is preferably 15 degree.
For anti-shunting ground structure first enters the inclined-plane, another advises setting, first end is formed by the circular cone outer circumferential face of two mutual transition with a chamfering radius rounding, one of them is right after one the second applying angle of relative first valve seat surface inclination of the second circular cone outer circumferential face after first valve seat surface, and another circular cone outer circumferential face is with respect to one first applying angle of first valve seat surface inclination.At this, the first applying angle be preferably 15 degree, and the second applying angle is preferably 7.5 degree in 5 to 10 degree scopes in 7.5 to 15 degree scopes.
Verified, if by transitional surface and first end section form first around seamed edge with minimum as far as possible rounding of angle radius rounding, all be favourable then for the formation of avoiding any stagnation pressure.In the ideal case, the configuration of a sharp edges should be set at this, but owing to the reason (endangering first seal ring) of manufacturing process and reality is next but unallowed.
According to another suggestion, annular groove in the valve chamber and transitional surface form first angle of yaw at an obtuse angle or right angle, wherein the angle of yaw at right angle (90 degree) is best, and this is because such most probable is guaranteed a kind of safe, the collisionless overflow of first closing component.Carry out rounding in this transition between groove and transitional surface with a cavetto radius.
For fear of form stagnation pressure when the first valve seat cleaning fluid enters the deflection plane of second closing component, another advise setting, by stop surface and deflection plane form second around seamed edge with second a rounding of angle radius rounding of minimum as far as possible.Because manufacturing process and reality, the transition portion of sharp-pointed seamed edge is unallowed in this zone, and a big relatively chamfering radius is disadvantageous and can causes forming undesirably stagnation pressure.
After leaving deflection plane, flow to the end face of intermediate seal circle or groove and form stagnation pressure for fear of the first valve seat cleaning fluid, also set, deflection plane with an axial undercutting apart from the undercutting end face.The profile of deflection plane in it flows out the some zone can be fitted with the end face of a relative groove in quadrupole deflector angle in this wise thus, make the valve seat cleaning fluid of winning just tangent with the intermediate seal circle, thus easily towards the deflection over there of second closing component, and subsequently can be along the wall curve of the adjacent face of groove, so that clean.If the quadrupole deflector angle in 5 to 20 degree scopes, is preferably 15 degree, then be proved to be favourable.
A kind of profile is proved to be and is most suited to first valve seat cleaning fluid guiding, this profile has a series of section, wherein first section, the 3rd section and be designed to rectilinear respectively by the 5th and last section that end face feeds, and these sections interconnect by second section and the 4th section, and wherein second section and the 4th section tangentially carry out rounding with first and one second a maximum as far as possible deflection radius to above-mentioned three sections.
Can reach a kind of flow results of satisfaction in the same way according to another suggestion, promptly profile is made up of a succession of curved section, and these sections have identical tangent line respectively on its corresponding transition point.Another form of implementation is set, and profile is made up of an independent section that changes curvature continuously.Also suggestion at last, profile is formed by an independent section with constant curvature.
Discharge detergent in order to ensure all perfect interference-free under any pressure and velocity conditions, set, the distolateral border near leaking the chamber of first closing component has a scarf, and this scarf is tilting towards discharge orifice on the side circumference entirely over there.What conform with purpose is that described scarf is designed to the circular cone outer circumferential face.Described circular cone outer circumferential face is with respect to its conical bottom face tilt 10 to 20 degree scopes, and 15 degree preferably tilt.
In order not only in the zone of the above-mentioned valve seat surface of double seated valve, to avoid forming turbulent flow and stagnation pressure, advantageously,, should be omitted in the every kind of unnecessary equipment or the obstacle that leak in the chamber as long as allow on the structure.At this, further suggestion, first movement rod that is connected with first closing component concentrically passes second that be connected with second closing component, as to be designed to a hollow stem movement rod, continue across discharge orifice, and first closing component away from the end of second closing component by at least one basically the crossbeam of radial directed be connected with first closing component securely.Avoided other pole and other link in this external leakage cavity region thus, and these parts are moved to one from leaking on the end quite far away, chamber, these parts can not have any interference influence to water conservancy diversion more there.
Further suggestion in this respect, three are fixedly installed on the movement rod section at equally distributed crossbeam on the circumference, these crossbeams respectively radial outside with one around annulus fixedly connected, and movement rod section, crossbeam and annulus form the weld assembly of a single-piece.More advantageously, weld assembly is welded on the pressure balance piston away from the border of the section that leaks the chamber of a qualification discharge orifice by annulus in the outside, and be welded on first movement rod by the movement rod section in the inboard, annulus is connected enlarged-diameter in this wise with its internal diameter with respect to the centre of the transition region of the conical expansion of discharge orifice and, makes the internal channel of discharge orifice do not dwindled by crossbeam.
Owing to removed the stop surface of the metal in the valve seat area of second closing component that still needs in the prior art so far by second design of the present invention, therefore with respect to known solution, in this zone, the structure of second closing component can have the more freedom degree.From the principle, can be provided with in this zone pure radially, radial/axial and also have second seal ring of possible pure axial action under certain condition.
In this respect, first kind of structure of the present invention set, and second valve seat surface is designed to columniform and is formed by annular groove, and second closing component has one second seal ring, and this second seal ring radially seals with slip joint with respect to second valve seat surface.In order to make second seal ring easily enter into second valve seat surface, to set relatively, second valve seat surface has a second end section of expanding towards second closing component (second enters the inclined-plane) over there.This second enters the inclined-plane and is fitted with one the 3rd applying angle with respect to second valve seat surface, and the described the 3rd closes the angle is preferably in 7.5 to the 15 degree scopes, is preferably 10 degree.
Because second seal ring comes out the process entering the inclined-plane from second, the sealing circle has experienced an elastic recovery distortion, this produces effect like this, so that it will be than with to enter the contacted ideal length in inclined-plane longer, can hinder mobile like this, so further suggestion, second enters the inclined-plane expands to one at it near end of second closing component and opens the inclined-plane, wherein opening the inclined-plane is fitted with an opening angle with respect to second valve seat surface, described opening angle is preferably in 35 to the 55 degree scopes, is preferably 45 degree.Realize a desirable cross section expansion by the zone of opening the inclined-plane at this, can reduce to show and guarantee the not interrupted needed second portion stroke of the second valve seat cleaning fluid.
A kind of second structure that relates to second valve seat surface is set, second valve seat surface is designed to conical and with respect to the cylinder shape groove angle of valve seat that tilts, and second closing component has one second seal ring, and this second seal ring axial/radial seals with slip/compressive engagement with respect to second valve seat surface.The described angle of valve seat is preferably 30 degree in 25 to 35 degree scopes.In order to reduce to guarantee the second portion stroke of the second valve seat cleaning fluid, set, second valve seat surface expands to one at it near end of second closing component and opens the inclined-plane, wherein opens the inclined-plane and fitted with an opening angle that has been quantized in the above with respect to cylinder shape groove.
According to the 3rd design suggestion according to the present invention, second valve seat surface is perpendicular to the longitudinal axis setting of double seated valve, and second closing component has one second seal ring, and this second seal ring axially seals with compressive engagement with respect to second valve seat surface.Yet, the solution of the valve seat disk advantage of a kind of such seal ring with pure axial action and pure axial action only is only feasible under the following conditions, be that the sealing circle is a ductility like this, so that under any condition, can both guarantee that second closing component clings on the transitional surface to Metal Contact securely or in case of necessity with its stop surface.
Description of drawings
In the accompanying drawing below the double seated valve that can clean valve seat as suggested in the present invention is described and sets forth by 26S Proteasome Structure and Function.Wherein:
Fig. 1 is of the present invention to clean the longitudinal sectional drawing of first kind of form of implementation of the double seated valve of valve seat, and just in valve seat area and with the bottom, wherein double seated valve is arranged on second closing component in its closed position and an intermediate seal circle;
Fig. 2 is according to the longitudinal sectional drawing of the amplification of the valve seat area of the double seated valve of Fig. 1;
The longitudinal sectional drawing of the valve seat area of the double seated valve of Fig. 3 Fig. 2 and two closing components, what wherein show is the open position of double seated valve, wherein double seated valve is in its open position;
The longitudinal sectional drawing of the double seated valve of Fig. 4 Fig. 2, wherein drive, that be positioned at the below, first closing component that is designed to sliding piston is in its valve seat cleaning position;
The longitudinal sectional drawing of the double seated valve of Fig. 5 Fig. 2, wherein related that drive, be positioned at second closing component top, that be designed to valve seat disk and be in its valve seat cleaning position;
Fig. 6 is of the present invention to clean the longitudinal sectional drawing of second kind of form of implementation of the double seated valve of valve seat, and one of them optional intermediate seal circle is set in place on first closing component of below, and double seated valve is on its closed position;
Fig. 7 a-7c is used for respectively illustrating enlarged view according to the profile of the valve seat area of second closing component of the double seated valve of Fig. 2 or Fig. 6;
Fig. 8 be used for according to the profile of the valve seat area of first closing component of the double seated valve of Fig. 2 or Fig. 6 and adjacent transitional surface the signal enlarged view;
Fig. 9 is at the signal enlarged view of the second closing component further groove at the profile of the regional and adjacent valve seat area of deflection plane;
The perspective view of Figure 10 a single type weld assembly, weld assembly comprises three crossbeams, they are fixedlyed connected a movement rod respectively with an annulus, be used for first valve rod connect with one be arranged on first closing component away from the pressure balance piston on the end of revealing the chamber; With
Figure 10 b comprises the vertical centre sectional drawing of composite structure of pressure balance piston, weld assembly and first movement rod of first closing component and indirect neighbor.
Embodiment
Double seated valve 1 of the present invention (Fig. 1) consists essentially of in first kind of form of implementation that valve chamber 10 with one first and one second valve chamber part 1a or 1b, two can move independently mutually has the movement rod 3a that matches respectively or closing component 3 and 4 and valve seat annulus 2 of 4a, and the valve seat annulus is set up connection by the open communication 2c in the inboard between valve chamber part 1a, 1b.
First closing component 3 (initiatively closing component) that is designed to sliding piston is contained on the closed position of double seated valve 1 among the first valve seat surface 2a who is formed by open communication 2c hermetically, and first valve seat surface is configured to columniform valve seat surface.For this reason, one first seal ring 6 is set in sliding piston 3, this first seal ring only passes through the deviation and the first valve seat surface 2a acting in conjunction (with the radial direction seal ring of slip joint) radially.Be designed to closed position and the second valve seat surface 2b acting in conjunction of second closing component 4 of sliding piston at double seated valve 1 equally, this second valve seat surface is designed to columniform and is formed by an annular groove 2d.Seal by one second seal ring 7, this second seal ring radially seals with slip joint with respect to the second valve seat surface 2b.
At illustrated closed position and open position (Fig. 3), two closing components 3,4 form one leakage chamber 5 betwixt, this leakage chamber is connected with the external world of double seated valve 1 by a discharge orifice 3d, and the middle respectively heart of this discharge orifice is passed a connected element 3b and a follow-up pressure balance piston 3c who is connected on this attachment portion who is connected on first closing component 3.
The common first movement rod 3a is fixedlyed connected with first closing component 3 by a plurality of starlike ground and at the gusset that passes discharge orifice 3d in the radial direction in the zone of first closing component.Because these gussets can have disadvantageous reaction to the flox condition and the flow pattern of leaking in the chamber 5, therefore in double seated valve 1 of the present invention, set, these are moved to the position that certain distance is arranged away from leakage chamber 5 with mechanically necessary tie points that three crossbeam 3e forms that are provided with evenly distributedly occur on circumference, preferably move on the end of pressure balance piston 3c away from first closing component 3.Form and the fixedlying connected of pressure balance piston by a circumferential annulus 3g, crossbeam 3e radial direction outer side is fixedlyed connected with this annulus.What conform with purpose is crossbeam 3e, annulus 3g and movement rod section 3a *Be combined into the weld assembly 30 of a single-piece.
Each closing component 3,4 all has a cylindrical projection 3 respectively in leakage chamber side *Or 4 *, its matching of the open communication 2c in valve seat annulus 2, partly be configured to the second throttle clearance D2 (also seeing Fig. 5) of the first throttle clearance D 1 (also seeing Fig. 4) and an annular of an annular.
Fig. 2 has shown in detail together with Fig. 1 to Fig. 5 and has been used for the details of double seated valve 1 valve seat area in its first kind of form of implementation.This double seated valve is characterised in that, an intermediate seal circle 8 is set on second closing component 4, and this intermediate seal circle seals closing component 3,4 in opening and closing movement process and at open position (Fig. 3) mutually.First closing component 3 has the cylindrical projection 3 of first diameter d 1 with it *(Fig. 4) and with the first valve seat surface 2a that open communication 2c matches form first throttle clearance D 1.Second closing component 4 has the cylindrical projection 4 of second diameter d 2 in the same way with it *(Fig. 5) the cylinder shape groove 2d with the annular of open communication 2c forms the second throttle clearance D2.
Half of diameter difference between the annular groove 2d and the first valve seat surface 2a (Fig. 2) is marked as a (radial width of transitional surface 2e).At this radially among a of elongated area, between the first valve seat surface 2a and annular groove 2d transitional surface 2e is set, wherein the cylindrical peripheral face of the end section of leading to the first valve seat surface 2a of transitional surface 2e and annular groove 2d forms preferably first angle of deflection (Fig. 5) at right angle.At this, annular groove 2d has a transition of leading to transitional surface 2e with cavetto radius r 1 rounding in open communication 2c, and wherein cavetto radius r 1 is r1＜a.The like this design of the size of radial width a, make one on the valve seat cleaning position of second closing component 4 from the second throttle clearance D2 enter leak chamber 5 the second valve seat cleaning fluid R2 (Fig. 5) on this transitional surface 2e towards the center of leaking chamber 5 deflection over there and flow through first closing component 3 safely and reliably.Can do not turned to first closing component 3 prematurely in order to ensure the second valve seat cleaning fluid R2, one by transitional surface 2e and first end section 2g form first around seamed edge U1 with the minimum as far as possible first rounding of angle radius r, 3 roundings, therefore formed clear and definite fluid breaker points in this.
By this measure, guaranteed not point to the valve seat area of first seal ring 6 from the second valve seat cleaning fluid R2 that the second throttle clearance D2 comes out.In addition, the radial width a of transitional surface 2e also must guarantee to realize a stop surface 2e who is used for second closing component 4 in the valve chamber side *(Fig. 2), so that realize second basic design of the present invention, promptly second closing component 4 firm (metal) backstop is close on valve seat annulus 2 and leaks chamber 5.Stop surface 2e in the valve chamber side *With one be arranged on second cylindrical projection 4 * End regions 4 *End face on stop surface 4e (also seeing Fig. 9) corresponding, from the radial direction, the width of this stop surface is b.Stop surface 2e in the valve chamber side *All be configured to linear with stop surface 4e in the closing component side; The cavetto radius r 1 of transitional surface 2e tangentially is connected to the stop surface 2e of valve chamber side *On.
Cylindrical projection 4 at second closing component 4 *End face on a central recess 4d (Fig. 2) is set, this groove radial outside start from a rotational symmetric deflection plane 4b and form there one second around seamed edge U2 (Fig. 5) and it distolateral by an end face 4c limited boundary that is substantially perpendicular to the longitudinal axis orientation of second closing component 4, wherein this deflection plane 4b leads to end face 4c with a quadrupole deflector angle β.Second the first end section 2g around seamed edge U2 (Fig. 5 and 2) next-door neighbour first valve seat surface 2a on the closed position of second closing component 4.From the vertical centre section, deflection plane 4b has a profile K who has no flex point curve, wherein profile K first section K1 in abutting connection with first end section 2g continues to extend through other section K2, K3 until Kn (Fig. 4), and in the end the direction vector on the end points of section K5 or Kn points to the discharge orifice 3d be arranged on first closing component, 3 centers, and does not collide with first closing component 3 in its zone that limits the zone of leaking 5 borders, chamber or intermediate seal circle 8 and form stagnation pressure.In order to make the first valve seat cleaning fluid R1 tangentially flow through (Fig. 4) from middle seal ring 8 next doors, deflection plane 4b is with an axial undercutting distance y undercutting end face 4c (Fig. 2).One of first closing component 3 has a safe distance x near distolateral border of leaking chamber 5 and the direction vector that enters first end section 2g at the exit point place of transitional surface 2e, and wherein said exit point is designed to above-mentioned first around seamed edge U1 (Fig. 5).
When the open position of double seated valve (Fig. 3), realize one and open stroke H completely, clearly, be arranged on intermediate seal circle 8 among the groove 4d and be used for being sealed in valve chamber 10 reliably and leak two closing components 3 and 4 between the chamber 5.
Fig. 2 clearly illustrates that the first section K1 is concordant with first end section 2g.Can be designed as the conical section (first enters the inclined-plane) of the outline elements that has independent bending or crooked and straight line at this first end section 2g, it is connected to the first valve seat surface 2a (also seeing Fig. 8) with a chamfering radius r2 and opens towards second closing component 4 over there.First end section 2g tilts with relative first a valve seat surface 2a of applying angle δ.This applying angle δ is preferably in 5 to the 15 degree scopes in 0 to 15 degree scope, preferably δ=15 degree.According to Fig. 8, a kind ofly be characterised in that with the further improved best first end section 2g that enters the inclined-plane form, first end section 2g is made of the circular cone outer circumferential face of two mutual transition with chamfering radius r2 rounding, and one of them is right after one second applying angle δ of the relative first valve seat surface 2a inclination of the second circular cone outer circumferential face 2g.2 of the first valve seat surface 2a 2, one first applying angle δ of the then relative first valve seat surface 2a inclination of another first circular cone outer circumferential face 2g.1 1The first applying angle δ 1In 7.5 to 15 degree scopes, best δ 1=15 degree, and the best δ in the second applying angle 2In 5 to 10 degree scopes, best δ 2=7.5 degree.In addition, show in Fig. 2 that the end face of first closing component 3 is provided with a scarf 3f inclination, conical over there towards discharge orifice 3d, wherein to become circular cone outer circumferential face and it be ζ with respect to inclination angle of inclination of circular cone bottom surface to this scarf preferred design.This inclination angle ζ is preferably in 10 to the 20 degree scopes, preferably ζ=15 degree.
After carrying out the stroke T1 of first portion, the first valve seat cleaning fluid R1 that comes out from first throttle clearance D 1 (Fig. 4) in the valve seat cleaning course of first closing component 3 is at first vertically along the first valve seat surface 2a perpendicular flow, not having shunting ground flows and has the deflection plane 4b that does not enter in groove 4d with impacting along with being designed to first curve that enters the first end section 2g on inclined-plane or circular cone outer circumferential face 2g.1 and 2g.2, and press profile K deflection there, leave the 5th and last section K5 (K5=Kn) with quadrupole deflector angle β, tangent with intermediate seal circle 8, abut in the zone that end face 4c went up and finally reached discharge orifice 3d basically tangently.
Can be clearly seen that the detailed curve of the profile K that has no flex point curve by Fig. 9.The first section K1, the 3rd a section K3 and the 5th and a last section K5 (K5=Kn) who is fed by end face 4c are designed to rectilinear respectively, and these sections K1, K3 and K5 interconnect by one second and one the 4th section K2, K4, and the second and the 4th section is tangentially with the maximum as far as possible first and second deflection radius r5, a r6 rounding.Clearly, the first section K1 is concordant with first end section 2g.In order to make the first valve seat cleaning fluid R1 (also seeing Fig. 4 at this) can not form stagnation pressure around seamed edge U2 place second, second be close to first end section 2g and with the second rounding of angle radius r, 4 roundings of minimum as far as possible around seamed edge on the closed position of second closing component 4.
Deflection plane 4b further constructs setting, and profile K forms (for example circular arc, elliptic arc, parabola, hyperbola) by a succession of curved section K1 to Kn, and they have identical tangent line respectively on the point of its corresponding transition.According to another structure, profile K is made up of an independent section (for example clearly limiting the curve of shape on helix or the another kind of mathematics) that changes curvature continuously.According to another suggestion, profile K is designed to an independent section (for example one section independent circular arc that has needed tangential entry and tangential outlet) with constant curvature.
Can make the first section K1 not concordant (seeing the curve [K1] among Fig. 9) fully with first end section 2g or 2g.1.Can allow first section [K1] fit, as long as the latter remains on below 15 degree with one second angle of yaw [ε].Otherwise can form stagnation pressure in second the zone around seamed edge U2.
If first end section 2g or 2g.1 are not designed to enter the inclined-plane, but follow the first valve seat surface 2a curve and until its end be designed to cylindrical (see curve among Fig. 9 2a} and K1}), then the first section K1 can be configured to concordant with first end section 2g, 2g.1 (seeing the curve of section [K1]) again, perhaps as shown in Figure 9, section { second angle of yaw { ε }＜15 degree of K1} shown in also first end section 2g, 2g.1 tilt relatively.
Second cylindrical projection 4 * End section 4 *After distolateral radial outside is right after stop surface 4e, have an annular ring around the second scarf 4f, its relative stop surface 4e extends with an angle of chamfer λ.By the scarf 4f and second cylindrical projection 4 *The outer circumferential face at second diameter d, 2 places form around stretch into the 3rd the form that zone design is a rounding around seamed edge U3.This angle of chamfer λ designs like this, make from radial direction, the 3rd around seamed edge U3 outwards move as far as possible far and as far as possible near-earth near transitional surface 2e by the curve of cavetto radius r 1 decision and there with transitional surface form an annular ring around alignment Z.By under any circumstance making second closing component 4 all fully concentric in this wise soon centering before entering into its stop dog position, even make that first and second still can be corresponding in needed mode around seamed edge U1, U2 when occurring making second closing component 4 wedging unexpectedly suddenly owing to insufficient guiding at each guiding point place that designs according to plan for this reason.
In the end of the leakage chamber side of the second throttle clearance D2 shown in Fig. 5 by the stop surface 2e of second closing component 4 recited above in the valve chamber side *On the stop dog position (see figure 4) closely closed (this is possible usually in principle) basically under the situation that the relative metal of metal reclines.The clean liquid of the first valve seat cleaning fluid R1 can not enter the second throttle clearance D2 again, can not enter the zone of second seal ring 7 then.Even under second seal ring, 7 situations badly damaged or that perhaps removed fully perhaps, clean liquid also no longer passes.
According to Fig. 5, after carrying out a second portion stroke T2, second closing component 4 is in its second valve seat cleaning position.At this, second seal ring 7 leaves with gap width and opens inclined-plane 2i, and second cylindrical projection 4 *Form the second throttle clearance D2 with annular groove 2d, by this second throttle clearance, but the second valve seat cleaning fluid R2 can be near second valve seat surface 2b overflow, that expose, and enters and leak chamber 5.The second valve seat surface 2b is designed to cylindrical and is formed by annular groove 2d.Second closing component 4 has second seal ring 7, and according to Fig. 2 (closed position), this second seal ring radially seals with slip joint with respect to the second valve seat surface 2b.
Can see obviously that from Fig. 5 and Fig. 7 a what the second valve seat surface 2b also had a protection seal ring enters inclined-plane 2h, wherein enter the inclined-plane with respect to the second valve seat surface 2b with one the 3rd applying angle δ 3Fitted the 3rd applying angle δ 3Be preferably in 7.5 to the 15 degree scopes, at this also best δ 3=15 degree.In order to reduce to be used for to expose the needed second portion stroke of circle second valve seat surface 2b T2, enter inclined-plane 2h with second and expand to the above-mentioned inclined-plane 2i that opens in its end near second closing component 4, wherein the latter with respect to the second valve seat surface 2b with an opening angle
Figure S2006800421894D00181
Fitted opening angle In 35 to 55 degree scopes, also best at this Degree.
The second valve seat cleaning fluid R2 at first leaves the second throttle clearance D2 (Fig. 5) along annular groove 2d, and by the center over there deflection of transitional surface 2e towards leakage chamber 5.Prevented press close to and direct the injection thus reliably to the valve seat area of first seal ring 6.In the valve seat cleaning course of second closing component 4, first closing component 3 is axially located like this, makes the second valve seat cleaning fluid R2 can flow through first closing component 3 in the clear.According to given pressure condition and under the influence of gravity, when double seated valve 1 disposes position shown in the figure, liquid jet presents a parabola shaped curve slightly, thereby tangentially flow through the end face of first closing component 3 that has its scarf 3f, this is desirable for cleaning technology.This water conservancy diversion and location by first closing component 3, even realized a kind of suction effect of the valve seat area of first seal ring 6, even thereby first seal ring 6 lose or the badly damaged situation under, do not have detergent yet and enter into the first adjacent valve chamber part 1a.
According to Fig. 7 b, the second valve seat surface 2b can also be designed to conical, and wherein it is with respect to angle of valve seat γ of cylinder shape groove 2d inclination.So second seal ring, 7 axial/radial of second closing component 4 seal with slip/compressive engagement ground with respect to the second valve seat surface 2b.Not needing one in the case is used for second of second seal ring 7 and enters the inclined-plane, in this case, what do not need to be used for second seal ring 7 opens inclined-plane 2f, yet the second valve seat surface 2b can be with the opening angle that has quantized there near the end of second closing component 4 at it
Figure S2006800421894D00184
Expand to the above-mentioned inclined-plane 2i that opens.
Double seated valve 1 according to the present invention also allows a kind of the second valve seat surface 2b to be designed to structure (Fig. 7 c) perpendicular to its longitudinal axis, and second seal ring 7 that wherein is arranged in second closing component 4 axially seals with compressive engagement with respect to this second valve seat surface 2b.Yet having only second seal ring 7 that ought axially work is ductility like this, so that the stop surface 2e of ground in importing to the transitional surface 2e region of the first valve seat surface 2a as before *On guarantee the stop dog position of second closing component 4, then above-mentioned solution is only possible.
Can see that from Fig. 6 second kind of form of implementation according to the present invention do not constitute qualification ground and have all inventive features of being set forth with first kind of form of implementation of the present invention, one of them optional intermediate seal circle 8 *Be arranged in first closing component 3.Optional intermediate seal circle 8 *Corresponding to the end face 4c of the groove 4d in second closing component 4 or in the case with its acting in conjunction.
The weld assembly 30 that has shown single-piece in Figure 10 a, this weld assembly is by movement rod section 3a *, three crossbeam 3e and annulus 3g form.Three at movement rod section 3a *Circumference on the crossbeam 3e that is provided with evenly distributedly fixedly connected with it.They respectively radial outside similarly with around annulus 3g fixedly connected.Weld assembly 30 the outside be welded on by annulus 3g limit discharge orifice 3d away from the pressure balance piston 3c on the border of the section that leaks the chamber on (seeing Figure 10 b), and be welded on the first movement rod 3a by movement rod section 3a* in the inboard.At this, connect in the centre under the transition region situation of a conical expansion, annulus 3g in this wise with respect to the enlarged-diameter of discharge orifice 3d, makes the internal channel of discharge orifice 3d do not dwindled by crossbeam 3e with its internal diameter.
The Reference numeral list
1 double-beat drop valve
10 valve chambers
The 1a first valve chamber part
The 1b second valve chamber part
2 valve seat annulus
2a first valve seat (cylinder valve seat surface)
2b second valve seat surface (axially; Radially; Axial/radial)
The 2c open communication
The 2d annular groove
The 2e transition face
2e ＊The stop surface of valve chamber side
2g first end section (first enters the inclined-plane)
2g.1 the first circular cone outer circumferential face
2g.2 the second circular cone outer circumferential face
2h the second end section (second enters the inclined-plane)
2i opens the inclined-plane
3 first closing components (sliding piston)
3 *First cylindrical projection
3a first movement rod
The 3b connected element
3c pressure balance piston
The 3d discharge orifice
The 3f scarf
30 weld assemblies
3a *The movement rod section
The 3e crossbeam
The 3g annulus
4 second closing components
4 *Second cylindrical projection
4 *End section
4a second movement rod
The 4b deflection plane
The 4c end face
The 4d groove
4e stop surface (in the closing component side)
4f second scarf
5 leak the chamber
6 first seal rings (radially)
7 second seal rings (axially; Radially; Axial/radial)
8 intermediate seal circles (on second closing component 4)
8 *Optional intermediate seal circle (on first closing component 3)
The radial width of a transitional surface
The b width is (in end section 4 *On the stop surface of closing component side)
D1 first diameter
D2 second diameter
R1 cavetto radius (transitional surface 2e's)
(first enters inclined-plane 2g to the r2 chamfering radius; 2g.1,2g.2)
The r3 first rounding of angle radius is (in the valve chamber side; Valve seat annulus 2)
The r4 second rounding of angle radius (second closing component 4)
R5 first deflection radius
R6 second deflection radius
The axial safe distance of x
The axial undercutting distance of y
α first angle of yaw
β quadrupole deflector angle
The γ angle of valve seat
δ applying angle (first enters inclined-plane 2g's)
δ 1The first applying angle (the first conical section 2g.1's)
δ 2The second applying angle (the second conical section 2g.2's)
δ 3The 3rd applying angle (second enters inclined-plane 2h's)
ε second angle of yaw
The ζ inclination angle
The λ angle of chamfer
Opening angle
D1 first throttle gap
D2 second throttle clearance
H opens stroke (fully open position) fully
The profile of K deflection plane 4b
K1 first section (first straightway)
The K2 first deflection radius r5
K3 the 3rd section (second straightway)
The K4 second deflection radius r6
K5 the 5th section (the 3rd straightway)
The last section of Kn
The R1 first valve seat cleaning fluid
The R2 second valve seat cleaning fluid
T1 first portion stroke (the first portion's open position/first valve seat cleaning position)
T2 second portion stroke (the second portion open position/second valve seat cleaning position)
U1 first is around seamed edge
U2 second is around seamed edge
U3 the 3rd is around seamed edge
The Z alignment

Claims (36)

1. double seated valve comprises two series connection closing components (3,4) that be provided with, relative movement mutually, and these two closing components prevent that on the closed position of double seated valve (1) fluid is from a valve chamber part (1a; 1b) to another valve chamber part (1b; 1a) overflow, these two closing components all limit a border of leaking chamber (5) at open position and closed position, this leakage chamber is connected with the external world of double seated valve (1), wherein on closed position, first closing component (3) that is designed to sliding piston is contained in each valve chamber part (1a that is interconnected hermetically; In open communication 1b) (2c), and open in the process of motion the intermediate seal circle (8 that acts on by between each closing component (3,4) at it; 8 *) abut in hermetically and attach troops to a unit on second closing component (4) of one second valve seat surface (2b), and further opening in the motion, second closing component is also transferred to an open position (H), wherein first closing component (3) has a seal ring (6), and the sealing circle radially seals with respect to cylindrical first valve seat surface (2a) that is formed in the open communication (2c); Each closing component (3,4) can be transferred to a valve seat cleaning position with gap width respectively by a partial journey independently of each other, so that wash its each homocentric valve seat surface (2a, 2b), wherein second closing component (4) can be transferred to its corresponding valve seat cleaning position by one with the second portion stroke (T2) of opening the motion equidirectional, and first closing component (3) can be transferred to its corresponding valve seat cleaning position by one with first portion's stroke (T1) of opening the reverse movement direction; One is arranged on cylindrical projection (3 on each closing component (3,4) leaking the chamber side *, 4 *) form the throttle clearance (D1 of an annular respectively with the open communication that matches (2c), D2), wherein first valve seat surface (2a) has a diameter, and this diameter is attached troops to a unit in the diameter of the annular groove (2d) of second closing component (4) less than one in open communication (2c); And between first valve seat surface (2a) and annular groove (2d), also have a transitional surface (2e),
It is characterized in that:
● second closing component (4) is arranged on its cylindrical projection (4 with one on its closed position *) end face on stop surface (4e) transitional surface (2e that reclines; 2e *) on, just be close to first valve seat surface (2a, 2g);
● at the cylindrical projection (4 of second closing component *) end face in a central recess (4d) is set, this central recess radial outside start from a rotational symmetric deflection plane (4b) and distolateral by end face (4c) limited boundary that is substantially perpendicular to the longitudinal axis orientation of second closing component (4), wherein deflection plane (4b) leads to the end face (4c) of central recess;
● deflection plane (4b) and stop surface (4e) form one second around seamed edge (U2), and this second is close to the first end section (2g) of first valve seat surface (2a) around seamed edge on the closed position of second closing component (4);
● from the vertical centre section, deflection plane (4b) has a profile (K) that has no flex point curve, wherein point to a middle heart and be arranged on discharge orifice (3d) on first closing component (3) at the direction vector on the outflow point of deflection plane (4b), and in the zone in those zones on border, chamber (5) is leaked in the qualification of first closing component (3) not with first closing component (3) and intermediate seal circle (8; 8 *) collide and form stagnation pressure;
● and one of first closing component (3) near the distolateral border of leaking chamber (5) be designed to the direction vector that one the first exit point place around seamed edge (U1) enters first end section (2g) of transitional surface (2e) and have an axial safe distance (x).
2. double seated valve according to claim 1 is characterized in that:
Intermediate seal circle (8) is arranged in the end face (4c) of central recess.
3. double seated valve according to claim 2 is characterized in that:
Described axial safe distance (x) all the foozle sums with each structural member of double seated valve (1) at least is the same big, these foozles decisions on the closed position of first closing component (3) first closing component (3) to the minimum axial direction distance of transitional surface (2e).
4. double seated valve according to claim 1 is characterized in that:
An intermediate seal circle (8 *) be arranged on the cylindrical projection (3 of first closing component (3) *) distolateral border on and with end face (4c) acting in conjunction of central recess.
5. double seated valve according to claim 4 is characterized in that:
To add an axial distance the same big with all foozle sums of each structural member of double seated valve (1) at least for described axial safe distance (x), first closing component (3) is to the minimum axial direction distance of transitional surface (2e) on the closed position of first closing component (3) in these foozle decisions, and intermediate seal circle (8) is from the cylindrical projection (3 of first closing component (3) *) distolateral border stretch out described axial distance.
6. according to the described double seated valve of one of claim 1 to 5, it is characterized in that:
Direction vector at described profile (K) starting point place is concordant with first end section (2g).
7. according to the described double seated valve of one of claim 1 to 5, it is characterized in that:
Depart from second angle of yaw (ε) at the direction vector at described profile (K) starting point place and the direction vector of first end section (2g) less than 15 degree.
8. according to the described double seated valve of one of claim 1 to 5, it is characterized in that:
First end section (2g) is designed to conical section, and this taper shape section is connected to first valve seat surface (2a) with a cavetto radius (r2) and opens towards second closing component (4) over there.
9. double seated valve according to claim 8 is characterized in that:
First end section (2g) is formed by at least one circular cone outer circumferential face.
10. double seated valve according to claim 9 is characterized in that:
Relative first valve seat surface of first end section (2g) (2a) inclination applying angle (δ).
11. double seated valve according to claim 10 is characterized in that:
Applying angle (δ) is in 0≤δ≤15 degree scopes.
12. double seated valve according to claim 9 is characterized in that:
First end section (2g) is formed by the circular cone outer circumferential face of two mutual transition with chamfering radius (r2) rounding, and one of them is right after one second applying angle (δ of second relative first valve seat surface of circular cone outer circumferential face (2g.2) (2a) inclination of first valve seat surface (2a) 2), one first applying angle (δ of another then relative first valve seat surface of circular cone outer circumferential face (2g.1) (2a) inclination 1), and the first applying angle (δ wherein 1) at 7.5≤δ 1In≤15 degree scopes, and the second applying angle (δ 2) at 5≤δ 2In≤10 degree scopes.
13., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
One by transitional surface (2e) and first end section (2g) form first around seamed edge (U1) with minimum as far as possible rounding of angle radius (r3) rounding.
14., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
Annular groove (2d) forms first angle of yaw (α) at an obtuse angle or right angle with transitional surface (2e).
15. double seated valve according to claim 14 is characterized in that:
Annular groove (2d) has a transition of leading to transitional surface (2e) with a cavetto radius (r1) rounding.
16., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
Second around seamed edge (U2) with second minimum as far as possible rounding of angle radius (r4) rounding.
17., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
Deflection plane (4b) is with the end face (4c) of axial undercutting distance (y) undercutting central recess.
18., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
Described profile (K) has a series of section (K1, K2, K3 ..., Kn), first section (K1), the 3rd section (K3) and by the end face (4c) of central recess feed the 5th to be that last section is designed to respectively rectilinear, and first section, the 3rd section and the 5th section (K1, K3, K5) by the second and the 4th section (K2, K4) interconnect, the second and the 4th section is tangentially with maximum as far as possible first deflection radius and one second deflection radius (r5, r6) rounding.
19., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
● described profile (K) by a succession of curved section (K1, K2, K3 ..., Kn) form, these sections have identical tangent line respectively on its corresponding transition point,
● perhaps profile (K) is made up of an independent section that changes curvature continuously,
● perhaps profile (K) is made up of an independent section with constant curvature.
20. double seated valve according to claim 18 is characterized in that:
The direction vector of last section (Kn) has a quadrupole deflector angle (β) with respect to the end face (4c) of central recess.
21., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
Discharge orifice (3d) will leak chamber (5) and be communicated with the external world of double seated valve (1), and the distolateral border near leaking chamber (5) of first closing component (3) has a scarf (3f), and this scarf tilts towards discharge orifice (3d) on full side circumference over there.
22. double seated valve according to claim 21 is characterized in that:
Scarf (3f) is designed to the circular cone outer circumferential face.
23. double seated valve according to claim 22 is characterized in that:
The circular cone outer circumferential face is with respect to an inclination angle of conical bottom face tilt (ζ).
24. double seated valve according to claim 23 is characterized in that:
First movement rod (3a) that is connected with first closing component (3) concentrically passes one and is connected, is designed to second movement rod (4a) of hollow stem with second closing component (4), continue across discharge orifice (3d), and first closing component (3) away from the end of second closing component (4) by at least one basically the crossbeam of radial directed (3e) be connected with first closing component securely.
25. double seated valve according to claim 24 is characterized in that:
Three on circumference equally distributed crossbeam (3e) be arranged on a movement rod section (3a regularly *) on, these crossbeams (3e) respectively radial outside with one around annulus (3g) fixedly connected and movement rod section (3a *), crossbeam (3e) and annulus (3g) form the weld assembly (30) of a single-piece.
26. double seated valve according to claim 25 is characterized in that:
Weld assembly (30) is welded to by annulus (3g) in the outside on the pressure balance piston (3c) away from the border of the section that leaks the chamber of a qualification discharge orifice (3d), and passes through movement rod section (3a in the inboard *) be welded on first movement rod (3a), and connect in the centre under the transition region situation of a conical expansion, annulus (3g) in this wise with respect to the enlarged-diameter of discharge orifice (3d), makes the internal channel of discharge orifice (3d) do not dwindled by crossbeam (3e) with its internal diameter.
27. double seated valve according to claim 1 is characterized in that:
Second valve seat surface (2b) is designed to columniform and is formed by annular groove (2d), and second closing component (4) has one second seal ring (7), and this second seal ring radially seals with slip joint with respect to second valve seat surface (2b).
28. double seated valve according to claim 27 is characterized in that:
Second valve seat surface (2b) has a second end section (2h) of expanding towards second closing component (4) over there.
29. double seated valve according to claim 28 is characterized in that:
The second end section (2h) with respect to second valve seat surface (2b) with one the 3rd applying angle (δ 3) fitted.
30., it is characterized in that according to claim 28 or 29 described double seated valves:
The second end section (2h) expands to one at it near end of second closing component (4) and opens inclined-plane (2i), wherein this open the inclined-plane with respect to second valve seat surface (2b) with an opening angle
Figure FSB00000362882200061
Fitted.
31. double seated valve according to claim 1 is characterized in that:
Second valve seat surface (2b) is designed to conical and with respect to annular groove (2d) angle of valve seat (γ) that tilts, and second closing component (4) has one second seal ring (7), and this second seal ring (7) axially and/or radially seals with slip and/or compressive engagement ground with respect to second valve seat surface (2b).
32. double seated valve according to claim 31 is characterized in that:
The angle of valve seat (γ) is in 25≤γ≤35 degree scopes.
33., it is characterized in that according to claim 31 or 32 described double seated valves:
Second valve seat surface (2b) expands to one at it near end of second closing component (4) and opens inclined-plane (2i), wherein this open the inclined-plane with respect to annular groove (2d) with an opening angle
Figure FSB00000362882200062
Fitted.
34., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
Second valve seat surface (2b) is perpendicular to the longitudinal axis setting of double seated valve (1), and second closing component (4) has one second seal ring (7), and this second seal ring axially seals with compressive engagement with respect to second valve seat surface (2b).
35., it is characterized in that according to the described double seated valve of one of claim 1 to 5:
The cylindrical projection (4 of second closing component *) end section (4 *) radial outside be right after stop surface (4e) have afterwards an annular ring around second scarf (4f), the relative stop surface of this second scarf (4e) extends with an angle of chamfer (λ), this angle of chamfer (λ) is design like this, make from radial direction a cylindrical projection (4 at second scarf (4f) and second closing component *) the part with second diameter (d2) between by rounding form the 3rd around seamed edge (U3) outwards move as far as possible far and as far as possible near-earth near transitional surface (2e) by the definite curve of cavetto radius (r1) and form there an annular ring around alignment (Z).
36. double seated valve according to claim 11 is characterized in that:
Applying angle (δ) is in 5≤δ≤15 degree scopes.
CN2006800421894A 2005-11-12 2006-02-18 Double seat valve Active CN101305228B (en)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
DE102005054123 2005-11-12
DE102005054123.2 2005-11-12
DE102005056624 2005-11-25
DE102005056624.3 2005-11-25
DE102005059709 2005-12-12
DE102005059709.2 2005-12-12
PCT/EP2006/001483 WO2007054131A1 (en) 2005-11-12 2006-02-18 Double seat valve

Publications (2)

Publication Number Publication Date
CN101305228A CN101305228A (en) 2008-11-12
CN101305228B true CN101305228B (en) 2011-05-04

Family

ID=40114359

Family Applications (2)

Application Number Title Priority Date Filing Date
CN2006800421894A Active CN101305228B (en) 2005-11-12 2006-02-18 Double seat valve
CN200680041956XA Active CN101305227B (en) 2005-11-12 2006-04-01 Double seat valve

Family Applications After (1)

Application Number Title Priority Date Filing Date
CN200680041956XA Active CN101305227B (en) 2005-11-12 2006-04-01 Double seat valve

Country Status (1)

Country Link
CN (2) CN101305228B (en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010030298A1 (en) * 2010-06-21 2011-12-22 Krones Aktiengesellschaft Multi-part valve disc
DE102010030300A1 (en) * 2010-06-21 2011-12-22 Krones Aktiengesellschaft Double seat valve and sealing of a double seat valve
DK2809974T3 (en) * 2012-02-03 2016-04-04 Gea Tuchenhagen Gmbh A process for the cleaning of the seat in a double-seat valve and the double seat valve for carrying out the method
JP6093442B2 (en) * 2012-06-16 2017-03-08 ゲーエーアー トゥーヘンハーゲン ゲーエムベーハー Double seat valve with valve seat cleaning function
EP2816266B1 (en) * 2013-06-21 2018-04-25 Alfa Laval Corporate AB Double seat valve
DE102015118001A1 (en) * 2015-10-22 2017-04-27 Vag-Armaturen Gmbh Absperrarmaturengehäuse
DE102015122309A1 (en) * 2015-12-18 2017-06-22 Voss Fluid Gmbh pipe connection
CN106090251B (en) * 2016-08-26 2018-09-28 成都欧浦特控制阀门有限公司 A kind of anti-wear valve core
CN106246940B (en) * 2016-08-26 2018-09-28 成都欧浦特控制阀门有限公司 A kind of plunger piston type valve core
CN106286867B (en) * 2016-08-26 2018-10-02 成都欧浦特控制阀门有限公司 A kind of spool for cylinder control valve
US10767520B1 (en) * 2019-08-19 2020-09-08 Caterpillar Inc. Valve seat insert for long life natural gas lean burn engines

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0174384A1 (en) * 1984-09-12 1986-03-19 Lavrids Knudsen Maskinfabrik A/S Double seat valve
CN1067723A (en) * 1991-06-07 1993-01-06 奥托·塔琴哈根有限公司及两合公司 Clean the control valve unit of method and this method of enforcement of double seated valve
CN1131456A (en) * 1993-09-22 1996-09-18 奥托·塔琴哈根有限公司及两合公司 Leak-free switching process for double seat valve and sealing arrangement for carrying out the process
DE19608792A1 (en) * 1996-03-07 1997-09-25 Tuchenhagen Gmbh Doubly-seated valve with cleanable seats plus two seals and leakage space

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE432982B (en) * 1980-04-24 1984-04-30 Alfa Laval Ab MIXING SAFETY VALVE

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0174384A1 (en) * 1984-09-12 1986-03-19 Lavrids Knudsen Maskinfabrik A/S Double seat valve
CN1067723A (en) * 1991-06-07 1993-01-06 奥托·塔琴哈根有限公司及两合公司 Clean the control valve unit of method and this method of enforcement of double seated valve
CN1131456A (en) * 1993-09-22 1996-09-18 奥托·塔琴哈根有限公司及两合公司 Leak-free switching process for double seat valve and sealing arrangement for carrying out the process
DE19608792A1 (en) * 1996-03-07 1997-09-25 Tuchenhagen Gmbh Doubly-seated valve with cleanable seats plus two seals and leakage space

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
CN 1067723 A,全文.

Also Published As

Publication number Publication date
CN101305227B (en) 2010-10-20
CN101305227A (en) 2008-11-12
CN101305228A (en) 2008-11-12

Similar Documents

Publication Publication Date Title
CN101305228B (en) Double seat valve
CA2626721C (en) Double seat valve
US8336572B2 (en) Double seat valve with seat cleaning
CN101371046A (en) A pump for pumping contaminated liquid including solid matter
US8459294B2 (en) Double-seat valve, the seats of which can be cleaned
US8622076B2 (en) Seat cleaning-capable double-seat valve
JPH01501889A (en) Methods and devices for controlling leakage cavities in valves
DK2861898T3 (en) DOUBLE SEAT VALVE WITH SEAT CLEANING FUNCTION
CN110145270A (en) Slip assemblies and bridge plug
US6499212B2 (en) Device and process for joining fitting parts on hollow profiles by means of fluid high internal pressure
US4389037A (en) Double disc gate vale with replaceable spacer ring
AU653324B2 (en) A fixed plate for a hydraulic valve, provided with means for ejecting chips
CN109973810B (en) Double-valve-body drain valve and assembling method thereof
US20100243073A1 (en) Double-seat valve having a seat-cleaning function, and method for cleaning said double-seat valve having a seat-cleaning function
US6687994B2 (en) Method for the manufacture of a welded rotor of a fluid-flow machine
ES2315850T3 (en) DOUBLE SEAT VALVE.
CN210738905U (en) Centrifugal pump formed by punching and welding
CN1875184B (en) Valve for a fuel injection pump
CN219924452U (en) Novel residual oil prevention air cavity
CN216741479U (en) Spiral-flow type gas sand anchor
KR101287882B1 (en) Nozzle tip of mud gun using eccentric ring
JPS6220422B2 (en)
CN218912804U (en) Pneumatic reverse circulation down-the-hole hammer drill bit for life rescue hole
US20210148470A1 (en) Hydraulic seal
CN100538248C (en) Compressor air cooler with replaceable flange ring

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
REG Reference to a national code

Ref country code: HK

Ref legal event code: DE

Ref document number: 1125990

Country of ref document: HK

C14 Grant of patent or utility model
GR01 Patent grant
REG Reference to a national code

Ref country code: HK

Ref legal event code: GR

Ref document number: 1125990

Country of ref document: HK