WO2007054131A1 - Doppelsitzventil - Google Patents
Doppelsitzventil Download PDFInfo
- Publication number
- WO2007054131A1 WO2007054131A1 PCT/EP2006/001483 EP2006001483W WO2007054131A1 WO 2007054131 A1 WO2007054131 A1 WO 2007054131A1 EP 2006001483 W EP2006001483 W EP 2006001483W WO 2007054131 A1 WO2007054131 A1 WO 2007054131A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- seat
- double
- closing member
- seat valve
- valve according
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/44—Details of seats or valve members of double-seat valves
- F16K1/443—Details of seats or valve members of double-seat valves the seats being in series
- F16K1/446—Details of seats or valve members of double-seat valves the seats being in series with additional cleaning or venting means between the two seats
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/4238—With cleaner, lubrication added to fluid or liquid sealing at valve interface
- Y10T137/4245—Cleaning or steam sterilizing
- Y10T137/4259—With separate material addition
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/87917—Flow path with serial valves and/or closures
- Y10T137/88022—One valve head provides seat for other head
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/87917—Flow path with serial valves and/or closures
- Y10T137/88038—One valve head carries other valve head
Definitions
- the invention relates to a double seat valve with two serially arranged, relatively movable closure members according to the preamble of claim 1.
- a double-seat valve of the generic type, which is due to its function, to allow cleaning of each exposed seat by gap-wide opening of its seats, also referred to as a seat-cleaning double seat valve, is known from DE 196 08792 C2.
- Each of the three seals in the known double seat valve is a discrete seal, with each seal having only a single function.
- the first seal in the first closing member is a purely radially acting seal, which slides in the first seat surface designed as a cylindrical lateral surface and seals there (seal with sliding engagement) as a result of the intended preload.
- the second seal in the second closing member acts either on the cone-shaped second seat, so that here can speak of an axially / radially acting seal (seal with pressure engagement), or it is also a purely radially acting seal provided (seal with sliding engagement).
- the fixed (metallic) stop for the limit stop of the second closing element (closed position) is also located on the second seat when a seal with pressure engagement is provided.
- the third seal, the so-called center seal then unfolds its effect when the first closing member comes into contact with the second closing member via this center seal during the opening stroke and in the course of the further opening movement carries the second closing member into the full open position (seal in pressure engagement).
- the center seal is arranged in a leakage cavity facing the end face on the second, depending driven closing member.
- the above briefly outlined known double seat valve has two so-called. Seat cleaning positions, wherein the first seat cleaning position is generated by a the opening stroke opposing first partial stroke. In this position, the leakage chamber on the first closing member arranged cylindrical projection forms with the associated cylindrical first seat a so-called. Throttle gap, via which the zoom out of the adjacent first valve body part detergent amount can be limited.
- the seat cleaning position of the second closing member is effected by a opening stroke rectified second partial stroke, wherein in the partially open position of the leakage chamber side arranged on the second closing member cylindrical projection with the associated part of the connecting opening forms a second throttle gap, which limits the amount generated in this seat cleaning second seat cleaning flow.
- the respectively assigned sections of the connecting opening are likewise different in diameter, so that a transitional surface is established between these two diameters.
- the first seat cleaning flow flows along the cylindrical seat surface and meets the frontal limit on the second closing member, wherein at least a direct impact of the first seat cleaning flow on the second throttle gap and thus the Seating area of the second closing member is prevented.
- the second seat cleaning flow at the diameter difference between the portions of the connection opening bridging the transition surface is deflected radially inwardly and past the upper end face boundary of the first closing member.
- such a double-seat valve is not only required to limit the amount of detergent and avoid direct application of the seat areas in the course of seat cleaning, but also to remove the seat cleaning flow as swirl-free as possible into the leakage cavity and / or there the environment, without the respective closed seating area is directly flowed by this seat cleaning flow or pressure increasing applied.
- Direct loading is understood to mean any velocity component from the respective seat cleaning flow that is directed perpendicularly to the walls delimiting the seat area. It has been found that any direct application in this regard leads to a conversion of kinetic flow energy into static pressure. Depending on the angle of impact of the
- Branch flow line Flow on the flowed wall or body surface results in a branch flow with a so-called "branch flow line", the latter dividing the flow into two halves
- the branch flow line itself runs on the so-called “stagnation point", so that at this point the velocity is zero is.
- the increase in pressure as a result of this stopping of the speed also receives the designation "back pressure.”
- the pressure-increasing mechanisms described above generate a leakage flow over the respective throttle gap and the defective or the completely no longer existing seat seal.
- Double-seat valves are furthermore known (WO 9854494 A1, EP 0 819 876 B1), which dispense with the aforementioned center seal.
- the radially acting first seat seal of the first closing member is moved into the second closing member in the course of the opening movement in a cylindrical, identical to the cylindrical seat surface of the first closing member, diameter-identical recess. Only then will the second
- the radial seal of the first closing member takes over the seal in the closed position and the function of the so-called.
- Middle seal in the pick-up and in the subsequent open position of the double seat valve which also acts purely radially in these positions, this first seat seal (sliding engagement ).
- the second closure member is formed as a seat plate, whose seal cooperates with a conical portion of the second seat, and it is also guided and centered on this conical portion. If the seal allows it, a fixed (metallic) stop for limiting the end position of the second closing element in the closed position of the double-seat valve is optionally provided on the conical section.
- the seat cleaning flow is guided along the cylindrical wall of the first seat and the adjoining recess and rebounds against the frontal boundary of the cylindrical recess, which is preferably perpendicular to the aligned cylindric oriented to the urban areas.
- Such a rectangular deflection of the flow is generally unfavorable, it triggers uncontrolled from the wall and creates vortexes and circulation flows, which can be accumulation pressure forming.
- the shape of the recess in the second closing member is determined by the shape and dimensions of the cylindrical seat in the valve housing. As a result, there are only limited possibilities for aerodynamic design of this leading the seat cleaning flow and steering recess.
- EP 0 819 876 B1 describes a double-seat valve which can be cleaned and in which likewise a discrete center seal is dispensed with and in which the first, first seat seal acting purely radially in the cylindrical valve seat has a double function.
- This double function consists in that the first seat seal arranged on the first closing element designed as a slide piston simultaneously has, in addition to a radial sealing function within the cylindrical valve seat, an axial sealing function with respect to the second closing element (pressure engagement).
- This axial sealing function is in turn effective when the first closing member passes in the course of the opening movement in a so-called. Pickup position with the second closing member and then transferred this also in an open position.
- the throttle gap on the first closing member is not arranged on the leakage chamber side but on the leakage side facing away from the double-seat valve according to EP 0 819 876 B1.
- the cylindrical approach to the formation of the candidate throttle gap with the associated surface of the connection opening is, based on the presentation position, below the first closing member.
- an annular recess in the connection opening is required, in which in the course of the associated seat cleaning this first seat seal is driven.
- the cylindrical projection on the first closure member then forms an attached arranged portion of the connection opening below this annular recess the desired throttle gap.
- the rearrangement of the throttle gap may be equivalent from a leakage-chamber side to a leakage-storage-remote position, however, this modification results in a critical cleaning situation for the first seat seal in the first closure member when the second closure member is transferred to its seat-cleaning position.
- the part of the double-seated seat gasket bridging the two aforesaid sealing areas is generally spaced from the cylindrical seating surface, thereby creating a sump-like, deep recess between the gasket and the cylindrical seating surface, which area constitutes a critical area for cleaning.
- the present invention is based on the basic features of the known double-seat valve according to DE 196 08 792 C2, in which case in particular the cylindrical lug arranged on the respective closing member for forming the respective throttle gap is used.
- the present invention utilizes the difference in diameter of these cylindrical lugs, which allows the formation of a transition surface between the different diameter portions of the connection opening associated with the cylindrical lugs.
- the principle of the separate center seal which has the task in the so-called pick-up position and the completion of the further opening movement to the open position to seal the two closing elements against each other is retained in each case, the solution according to the invention in terms of the position of the center seal by no means only one of the two possible arrangements is established.
- the solution according to the invention allows either the arrangement of the center seal in the end face of the second closing member or alternatively in the end face of the first closing member.
- a first inventive concept is to initiate the seat cleaning flow emerging from the associated throttle gap during the respective seat cleaning as fluidly as possible into the leakage cavity and away from it in the same way into the environment. This succeeds on the one hand by a new, the seat cleaning flows in the leakage cavity leading and directing flow contour. With the seat cleaning of the lower, first closing element, this new flow contour ensures that the first seat cleaning flow follows the course of the wall in the area of the first seat without separation.
- the central recess is essentially formed by a rotationally symmetrical deflection surface which begins radially on the outside at the end face of the second closing element in question and which is delimited by an end face oriented essentially perpendicular to the longitudinal axis of the second closing member, the deflection surface being delimited in the End face opens.
- Essential is the bumpless deflection of the seat cleaning flow in the deflection. This is achieved according to the invention in that, seen in the meridian section, the deflection surface has a contour with kink-free course, wherein a direction vector in the Ausmündungsyak the deflection under the vorg. Conditions in the centrally disposed in the first closing member drain hole points. It is also essential that at the starting point of the contour, a second peripheral edge is formed, which is directly adjacent to a first end portion of the first seat in the closed position of the second closing member.
- the second seat cleaning flow generated by ventilating the second closing member it is essential that it detachably delineate at a first peripheral edge formed by the transitional surface and the first end portion of the first seating surface and tangentially guided past the first closing member in the area of the leakage cavity ,
- a safety distance is provided between the first peripheral edge and the areas of the first closing element in question. see, which prevents a relevant impingement under all possible technical conditions.
- a second inventive basic idea is to make the end position limit of the second closing member (spool with radially acting seal in sliding or possibly seat plate with radial / axial acting seal in sliding / pressure engagement) in its closed position not on the cooperating with the seal seating area, such as This is the case regularly with known double-seat valves of the generic type, but the desirable, but not realized in all cases or realizable solid (metallic) stop of the second shooting member to the seal facing away from the end of the associated throttle gap to relocate.
- This is achieved according to the invention in that, in its closed position, the second closing element rests against the transition surface with a stop surface arranged on an end face of its cylindrical projection, namely directly adjacent to the first seating surface.
- the end section of the second cylindrical projection is configured radially on the outside following the stop surface in such a way that an annular circumferential centering point is formed here.
- This centering point is, as seen in the radial direction, as far as possible shifted outwards and brought as close as possible to the determined by a radius of curvature course of the transition surface.
- This is achieved by an annular circumferential second chamfer which is provided at the end portion and which extends against the abutment surface at a chamfer angle and which, together with the second diameter of the second cylindrical projection, produces a rounded peripheral edge ensuring centering in the transition surface forms.
- the center seal is arranged in the end face of the second closing member, wherein here a point in the end face of the recess radially inward of the deflection surface comes into question.
- care must be taken to ensure that the deflection function of the deflection surface formed primarily by the recess for the first seat cleaning is ensured and the first seat cleaning flow in its further course at the center seal does not experience any obstruction in such a way that vortex formation and detachment phenomena occur in the leakage cavity that can lead to local dynamic pressure formation.
- the first closing member provides in the present case on an associated surface of its end portion a sealing surface for this central seal.
- Another proposal provides to arrange an alternative center seal in the frontal boundary of the cylindrical projection of the first closing member, this alternative center seal then preferably with the end face the recess cooperates in the second closing member, with a region radially inward of the deflection surface.
- this alternative center seal then preferably with the end face the recess cooperates in the second closing member, with a region radially inward of the deflection surface.
- other contact points are also possible, and the deflection itself is not ruled out.
- Another proposal provides that a direction vector at the starting point of the contour of the deflection surface is aligned with the first end portion of the first seat surface.
- This preferred embodiment ensures a largely bumpless entry of the first seat cleaning flow in the deflection and thus in the recess in the second closing member.
- the abovementioned condition is to be observed both for a cylindrical end section which is in alignment with the cylindrical first seat surface and for a conically widening first end section (a so-called insertion bevel) which is likewise provided in the context of the invention.
- the conically widening end section can have exclusively curved or curved and straight contour elements.
- first insertion bevel forming first end portion by at least one conical surface. So that the first seat cleaning flow does not detach on the contour of this conical surface, it is proposed to incline the first end section by an angle of attack which is in the range between 0 and 15 degrees, preferably in the range between 5 and 15 degrees and here again preferably at 15 degrees is executed.
- the first end section is formed by two conical lateral surfaces rounded off with a rounding radius, wherein a second conical surface immediately adjoining the first seat surface is at a second angle of attack against the first seat surface and the other cone shroud are inclined at a first angle of attack against the first seating surface.
- the first angle of attack in the range 7.5 to 15 degrees, preferably 15 degrees and the second angle of attack in the range 5 to 10 degrees, preferably designed with 7.5 degrees.
- the annular recess in the housing forms with the transition surface a blunt or a vertical first Um- Steering angle, wherein the vertical deflection angle (90 degrees) is preferred, as this safe, collision-free overflow of the first closing member is most likely ensured.
- the transition between the recess and the transition surface is rounded with a fillet radius.
- the deflecting surface undercuts the end face by an axial undercut distance.
- the contour of the deflection surface in the region of its Ausmündungsconces so employed by a fourth deflection with respect to the end face of the recess are that the first seat cleaning flow the center seal just tangent, thereby slightly deflected towards the second closing member and then the wall of the adjacent End face of the recess for the purpose of cleaning the same can follow. It has proved to be expedient if the fourth deflection angle is carried out in the range of 5 to 20, preferably 15 degrees.
- a contour has proven to have a sequence of sections, wherein the first sections, the third section and the fifth and last section opening out from the end face are respectively rectilinear, and wherein these sections over the second and the fourth section, the three aforementioned round off tangentially with the largest possible first and second deflection radius, are interconnected.
- contour is composed of a sequence of curved sections which each have a common tangent at their respective transition points.
- Another embodiment provides that the contour consists of a single section of continuously changed curvatures.
- the contour is formed from a single section of constant curvature.
- the front-side boundary of the first closing element facing the leakage cavity has an incline which slopes all the way to the drain hole.
- This chamfer is suitably designed as a conical surface, which is inclined relative to the base of the cone in the range of 10 to 20 degrees, preferably 15 degrees.
- the weld-on part adjoins the first adjusting rod on the outside via the ring to a pressure-compensating piston delimiting an annular cavity of the drain bore and on the inside via the adjusting rod section to the first adjusting rod and if the ring in its inner diameter in relation to the diameter of the drain hole and the Intermediate connection of a conically widening transition region is increased, that the inner passage of the drain hole is not diminished by the trusses.
- Closing member In principle, in this area purely radial, radial / axial and, to a limited extent, also purely axially acting second seals can be provided.
- the invention according to a first embodiment provides that the second seat is cylindrical and formed by the annular recess, that the second closing member has a second seal which seals radially relative to the second seat in sliding engagement.
- the second seat has a second end portion (second retraction slope) which widens toward the second closing member.
- This second Einfahrschräge is compared to the second seat around a third angle of attack, preferably in the range of 7.5 to 15 degrees, preferably employed at 10 degrees.
- the second seal undergoes an elastic recovery deformation when extending out of the second Einfahrschräge, which acts so that it remains in flow-impeded contact with the Einfahrschräge longer than is desirable, provides a further proposal that the second Einfahrschräge at her the second end member facing the opening in an opening bevel, the latter opposite the second seat by an opening angle, preferably in the range of 35 to 55 degrees, preferably set at 45 degrees.
- an opening angle preferably in the range of 35 to 55 degrees, preferably set at 45 degrees.
- a second embodiment relating to the second seat provides that the second seat is tapered and inclined relative to the cylindrical recess by a seat angle, and that the second shutter has a second seal axially / radially opposed to the second seat in sliding / pressure engagement seals.
- the seat angle is in this case carried out in the range between 25 and 35 degrees, preferably with 30 degrees.
- the second seat expands at its end facing the second closing element into an opening bevel, the latter being set opposite the cylindrical recess by an opening angle already quantified above.
- the second seat surface is arranged perpendicular to the longitudinal axis of the double seat valve, and that the second closing member has a second seal which seals axially relative to the second seat surface in pressure engagement.
- Embodiments of the proposed double-seat valve according to the invention which can be cleaned according to the invention are shown in the drawing and are described below with regard to design and function. Show it
- Double seat valve in a first embodiment, in the seating area and below it, wherein the double seat valve is in its closed position and a center seal is arranged in the second closing member;
- Figure 2 in longitudinal and detail an enlarged view of
- FIG 3 in the longitudinal and detail of the seating area and the two closing members of the double seat valve according to Figure 2, wherein this is in its open position;
- Figure 4 in the longitudinal and detail of the double seat valve according to Figure 2, wherein the independently driven, located below, designed as a slide piston first closing member is in its seat cleaning position;
- Figure 5 in the longitudinal and detail of the double seat valve according to Figure 2, wherein the dependent driven, overhead, designed as a slide piston second closing member is in its seat cleaning position;
- 6 shows in longitudinal and detail the seat-cleaning double-seat valve according to the invention in a second embodiment, with an alternative central seal in the lower lying, first closing member is arranged and the double-seat valve is in its closed position;
- FIGS 7a - 7c respectively in a schematic and enlarged view of the contour of the seat portion for the second closing member of the double seat valve according to Figure 2 or Figure 6;
- 10a shows a perspective view of a one-piece welding part, consisting of three an adjusting rod with a ring each firmly connecting trusses, for connecting the first valve rod with a laxative cavity remote from the end of the first closing member pressure equalizing piston and
- Figure 10a in Meridianburg the composite construction of the first closing member and indirectly adjacent pressure equalizing piston, welding part and first valve rod.
- the double-seat valve 1 (FIG. 1) according to the invention in a first embodiment essentially consists of the valve housing 10 with a first and a second valve housing part 1a or 1b, the two independently movable closing members 3 and 4 with the respectively associated adjusting rods 3a and 4a and a seat ring 2, which establishes a connection between the valve housing parts 1 a, 1 b via an inside connection opening 2 c.
- the first closing element 3 active closing element designed as a slide piston is sealingly received in a first seating surface 2a formed by the connecting opening 2c, which is designed as a cylindrical seating surface.
- a first seal 6 is provided in the spool 3, which cooperates exclusively by radial bias with the first seat 2a (radial seal in sliding engagement).
- the second closing element 4 which is likewise designed as a slide piston, interacts with a second seat surface 2b, which is cylindrical and formed by an annular recess 2d.
- the sealing takes place via a second seal 7, which seals radially in relation to the second seat surface 2b in sliding engagement.
- the two closing members 3, 4 form both in the illustrated closed and in an open position ( Figure 3) between them a leakage cavity 5, which has a drain hole 3d, which adjoins the first closing member 3 connecting part 3b and a to the latter continuing pressure equalization piston 3c each centrally penetrates, is connected to the environment of the double seat valve 1.
- the firm connection with the latter takes place via a circumferential ring 3g, with which the trusses 3e are firmly connected radially on the outside.
- Each closing member 3, 4 has on the leakage chamber side a cylindrical projection 3 * or 4 * which, with the associated part of the connection opening 2c in the seat ring 2, has an annular first throttle gap D1 (see also FIG. 4) or an annular second throttle gap D2 (see also FIG. 5).
- Figures 2 to 5 illustrate in conjunction with Figure 1 details of the seating area for the double seat valve 1 in its first embodiment.
- the latter is u.a. characterized in that a center seal 8, which the Schstedglie- 3, 4 in their opening and closing movement and in the open position
- the first closing member 3 forms, with its cylindrical projection 3 * (FIG. 4), which has a first diameter d1, and with the associated first seating surface 2a of the connection opening 2c, the first throttle gap D1.
- the second closing member 4 forms in the same way with its second cylindrical projection 4 *
- FIG. 5 which has a second diameter d2, together with the annular, cylindrical recess 2d in the connection opening 2c, the second throttle gap D2.
- a (radial width of a transition surface 2e) Half the difference in diameter between the annular recess 2d and the first seat 2a (FIG. 2) is indicated by a (radial width of a transition surface 2e).
- the transition surface 2e is provided between the first seat surface 2a and the annular recess 2d, the end section of the transition surface 2e opening into the first seat surface 2a forming a preferably perpendicular first deflection angle ⁇ with the cylindrical surface of the annular recess 2d ( Figure 5).
- the annular recess 2d in the connection opening 2c has a rounded transition with the radius of curvature r1 to the transition surface 2e, the radius of curvature r1 being carried out with r1 ⁇ a.
- the radial width a is made so large that a in the seat cleaning position of the second closing member 4 from the second throttle gap D2 in the leakage cavity 5 exiting second seat cleaning flow R2 ( Figure 5) at the transition surface 2e to the center of the leakage cavity 5 and safely over the first closing member 3 is deflected away.
- a first peripheral edge U1 formed by the transitional surface 2e and a first end portion 2g is rounded off with a smallest possible first corner rounding r3, thereby defining a defined one Stall parts arise.
- the radial width a of the transition surface 2e must also ensure the realization of a valve housing side stop surface 2e * ( Figure 2) for the second closing member 4, so that the second inventive idea, namely a leakage (5) immediately adjacent solid (metallic) stop of the second closing member 4 on the seat ring 2, is to be realized.
- the valve housing-side abutment surface 2e * corresponds to a provided on the end face of an end portion 4 ** of the second cylindrical projection 4 * stop surface 4e (see also Figure 9), which, seen in the radial direction, has a width b.
- the valve housing side abutment surface 2e * and the closing member side abutment surface 4e are each rectilinear; the radius of curvature r1 of the transition surface 2e connects tangentially to the stop surface 2e *.
- a central recess 4d is provided (FIG. 2), which begins radially on the outside with a rotationally symmetrical deflection surface 4b and forms a second peripheral edge U2 (FIG. 5) and which is essentially a front side is limited perpendicular to the longitudinal axis of the second closing member 4 oriented end face 4c, wherein the deflection surface 4b opens with a fourth deflection angle ß in the end face 4c.
- the second peripheral edge U2 directly adjoins the first end section 2g of the first seating surface 2a.
- the deflecting surface 4b has a contour K with kink-free course, with a first section K1 of the contour K adjacent to the first end section 2g continuing over further sections K2, K3 through Kn (FIG. 4) and the direction vector in the end section of the last section K5 or Kn in the centrally arranged in the first closing member 3 drain hole 3d points, without colliding with the first closing member 3 in the region of its the leakage cavity 5 bounding areas or the center seal 8 forming back pressure.
- a first seat cleaning flow R1 to be able to pass tangentially past the center seal 8 (FIG.
- the deflection surface 4b undercuts the end face 4c by an axial undercut distance y (FIG. 2).
- An end boundary of the first closing member 3 facing the leakage cavity 5 has an axial safety distance x from the direction vector at the exit point of the transition surface 2e into the first end portion 2g, which is formed as the first peripheral edge U1 mentioned above (FIG. 5).
- Figure 2 illustrates that the first portion K1 is aligned with the first end portion 2g.
- the first end portion 2g may be formed as a conical portion (first Einfahrschräge) with exclusively curved or curved and straight contour elements, which adjoins the seat surface 2a with a rounding radius r2 (see also Figure 8) and opens to the second closing member 4 out ,
- the first end portion 2g is inclined by an angle of attack ⁇ against the first seat 2a.
- a further optimization of the first end portion 2g in the form of a further improved insertion slope is characterized according to Figure 8 in that the first end section 2g is formed by two conical lateral surfaces rounded into one another with the rounding radius r2, wherein a second conical surface 2g.2 immediately adjoining the first seat surface 2a has a second angle of attack ⁇ 2 against the first seat surface 2a and the other conical surface 2g. 1 are inclined at a first angle ⁇ 1 against the first seating surface 2a.
- the end face of the first closing element 3 is provided with a sloping, conical bevel 3f towards the drainage bore 3d, the latter preferably being designed as a conical surface and inclined relative to the base surface of the cone by an inclination angle ⁇ .
- the first seat cleaning flow R1 emerging from the first throttle gap D1 (FIG. 4) during the seat cleaning of the first closing element 3 initially flows perpendicularly along the first seat surface 2a, following the path of the first end section 2g or first stop ramp formed
- the conical defects 2g.2, 2g.1 without detaching and occurs bumplessly in the deflection surface 4b in the recess 4d, where it is deflected according to the contour K, leaves the fifth and last section K5 (K5 Kn) with the fourth deflection angle ß , touches the center seal 8, applies largely tangentially to the end face 4c and finally enters the region of the drain hole 3d.
- the more detailed profile of the contour K with kink-free course can be seen in detail from FIG.
- the first section K1 is aligned with the first end section 2g. So that the first seat cleaning flow R1 (see also FIG. 4) can not form a dynamic pressure at the second peripheral edge U2, the latter directly adjoins the first end section 2g in the closed position of the second closing element 4 and is rounded off with the smallest possible second corner rounding r4.
- a further embodiment of the deflection surface 4b provides that the contour K consists of a sequence of curved sections K1 to Kn (for example circular arcs, ellipses, parabolas, hyperbolas) which each have a common tangent at their respective transition points.
- the contour K is formed from a single section of continuously changed curvature (e.g., spiral or other mathematically closed waveform).
- the contour K is designed according to another proposal with a single section of constant curvature (for example, a single circular arc with the required tangential entry and exit).
- the first section K1 can again be designed to be flush with the first end section 2g, 2g.1 (see the course of the section [K1]), or else, as FIG. 9 shows, as the section ⁇ K1 ⁇ around the said second deflection angle ⁇ . ⁇ 15 degrees against the first end portion 2g, 2g.1 be inclined.
- the end section 4 ** of the second cylindrical projection 4 * has an annular, circumferential second bevel 4f on the end face radially outside, following the stop face 4e, which runs against the stop face 4e at a bevel angle ⁇ .
- the peripheral penetration area formed by the chamfer 4f and the lateral surface of the second cylindrical projection 4 * at the second diameter d2 is in the form of a rounded third peripheral edge U3.
- the Anschrägungswinkel ⁇ is dimensioned such that the third circumferential edge U3, as seen in the radial direction, as far as possible displaced outwards and as close as allowed to the determined by the radius of curvature r1 course of the transition surface 2e is introduced and there with the latter an annular circumferential Centering point Z forms.
- the second closing element 4 is centered sufficiently coaxially in each case just before it enters its stop position such that the first and the second peripheral edge U1, U2 correspond in the necessary manner, even if an unscheduled tilting of the second closing element 4 due to deficient Leadership should occur at the planned management points for this purpose once.
- the leakage-chamber-side end of the second throttle gap D2 denoted in FIG. 5 is largely tightly closed by the stopper position (see FIG. 4) of the second closing member 4 on the valve-housing-side stop face 2e * (as far as is fundamentally possible in the case of a metal-to-metal system is).
- Cleaning liquid of the first seat cleaning flow R1 can no longer enter the second throttle gap D2 and thus into the region of the second seal 7. Even with possibly severely damaged or possibly completely removed second seal 7 therefore no passage for cleaning liquid is given more.
- the second closing element 4 assumes its second seat cleaning position after completion of a second partial stroke T2.
- the second seal 7 is thereby far apart from an opening bevel 2i, and the second cylindrical projection 4 * together with the annular recess 2d the second throttle gap D2, through which the second seat cleaning flow R2 to the now überströmbare, exposed seat 2b and introduced into the leakage cavity 5 can be introduced.
- the second seat 2b is made cylindrical and is formed by the annular recess 2d.
- the second closing member 4 has the second seal 7, which, as shown in FIG. 2 (closed position), seals radially in relation to the second seating face 2b in sliding engagement.
- the second seat cleaning flow R2 first leaves the second throttle gap D2 (FIG. 5) along the annular recess 2d and is deflected via the transition surface 2e to the center of the leakage cavity 5. A direct and direct spraying of the seat portion of the first seal 6 is thereby reliably prevented.
- the first closing member 3 is axially positioned in the seat cleaning of the second closing member 4 such that the second seat cleaning flow R2 can flow unhindered over the first closing member 3.
- the liquid jet takes a slightly parabolic course, so that the end face of the first closing member 3 is tangentially overflowed with its bevel 3f, which is desirable for cleaning reasons.
- the second seat 2b can also be designed cone-shaped according to Figure 7b, wherein it is inclined relative to the cylindrical recess 2d by a seat angle ⁇ .
- the second seal 7 of the second closing member 4 then seals axially / radially with respect to the second seat 2b in sliding / pressure engagement.
- a second insertion bevel for the second seal 7 is not required in this case, however, the second seat 2b can expand at its end facing the second closing member 4 in the opening bevel 2i described above with the opening angle ⁇ quantified there.
- the double-seat valve 1 also permits a configuration of the second seat 2b perpendicular to its longitudinal axis (FIG. 7c), wherein the second seal 7 arranged in the second closing member 4 seals axially with respect to this second seat 2b in pressure engagement.
- this solution is only possible if the axially acting second seal 7 is so ductile that the stop position of the second closing member 4 is still ensured on the stop surface 2e * in the area of the transition area 2e exiting into the first seating surface 2a.
- the seat-cleanable double-seat valve 1 according to the invention in its second embodiment, in which an alternative center seal 8 * is arranged in the first closing member 3, has all features essential to the invention described in connection with the first embodiment.
- the alternative center seal 8 * corresponds and acts in this case with the end face 4c of the recess 4d in the second closing member 4 together.
- FIG. 10 a shows the one-piece weld-on part 30, which is formed from the adjusting rod section 3 a *, the three trusses 3 e and the ring 3 g.
- the three evenly distributed over the circumference of the Verstellstangenabitess 3a * arranged trusses 3e are firmly connected to this. They are also radially outwardly also firmly connected to the circumferential ring 3g.
- the weld-on part 30 is welded on the outside via the ring 3g to the pressure-compensating piston 3c delimiting the leakage-cavity-remote section of the drainage bore 3d (see Fig. 10b) and internally via the adjustment rod section 3a * to the first adjustment rod 3a.
- the ring 3g is enlarged in its inner diameter with respect to the diameter of the drainage bore 3d with the interposition of a conically widening transitional region such that the inner passage of the drainage bore 3d is not narrowed by the crossbars 3e.
- r1 Rounding radius (the transition surface 2e)
- r2 Rounding radius (first entrance slope 2g; 2g.1, 2g.2)
- r3 first corner rounding (housing side, seat ring 2)
- second corner rounding (second closing element 4)
- r5 first deflection radius r ⁇ second deflection radius
- first deflection angle ß fourth deflection angle ⁇ seat angle ⁇ angle of attack (the first Einfahrschräge 2g) ⁇ t first angle (first conical section 2g.1) ⁇ 2 second angle (second conical section 2g.2) ⁇ 3 third angle of attack (the second Einfahrschräge 2h) ⁇ second deflection ⁇ inclination angle ⁇ bevel angle ⁇ opening angle
- T1 first partial lift (first partial open position / first seat cleaning position)
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Lift Valve (AREA)
- Fluid-Driven Valves (AREA)
- Taps Or Cocks (AREA)
- Materials For Photolithography (AREA)
- Details Of Valves (AREA)
Abstract
Description
Claims
Priority Applications (10)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200650003492 DE502006003492D1 (de) | 2005-11-12 | 2006-02-18 | Doppelsitzventil |
AT06707068T ATE428879T1 (de) | 2005-11-12 | 2006-02-18 | Doppelsitzventil |
CN2006800421894A CN101305228B (zh) | 2005-11-12 | 2006-02-18 | 双座阀 |
EP06707068A EP1945975B1 (de) | 2005-11-12 | 2006-02-18 | Doppelsitzventil |
JP2008539265A JP5147706B2 (ja) | 2005-11-12 | 2006-02-18 | ダブルシートバルブ |
US11/659,108 US7905253B2 (en) | 2005-11-12 | 2006-02-18 | Double seat valve |
AU2006312793A AU2006312793A1 (en) | 2005-11-12 | 2006-02-18 | Double seat valve |
DK06707068T DK1945975T3 (da) | 2005-11-12 | 2006-02-18 | Dobbeltsædet ventil |
CA 2571244 CA2571244C (en) | 2005-11-12 | 2006-02-18 | Double seat valve |
HK09103719A HK1125990A1 (en) | 2005-11-12 | 2009-04-22 | Double seat valve |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005054123.2 | 2005-11-12 | ||
DE102005054123 | 2005-11-12 | ||
DE102005056624.3 | 2005-11-25 | ||
DE102005056624 | 2005-11-25 | ||
DE102005059709 | 2005-12-12 | ||
DE102005059709.2 | 2005-12-12 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007054131A1 true WO2007054131A1 (de) | 2007-05-18 |
Family
ID=36604249
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2006/001483 WO2007054131A1 (de) | 2005-11-12 | 2006-02-18 | Doppelsitzventil |
PCT/EP2006/002989 WO2007054134A1 (de) | 2005-11-12 | 2006-04-01 | Doppelsitzventil |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2006/002989 WO2007054134A1 (de) | 2005-11-12 | 2006-04-01 | Doppelsitzventil |
Country Status (10)
Country | Link |
---|---|
US (2) | US7905253B2 (de) |
EP (2) | EP1945975B1 (de) |
JP (2) | JP5147706B2 (de) |
AT (2) | ATE428879T1 (de) |
AU (2) | AU2006312793A1 (de) |
CA (2) | CA2571244C (de) |
DE (2) | DE502006003492D1 (de) |
DK (2) | DK1945975T3 (de) |
HK (1) | HK1125990A1 (de) |
WO (2) | WO2007054131A1 (de) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2008151763A1 (de) | 2007-06-14 | 2008-12-18 | Tuchenhagen Gmbh | Sitzreinigungsfähiges doppelsitzventil |
DE102007027765A1 (de) | 2007-06-16 | 2008-12-18 | Tuchenhagen Gmbh | Doppelsitzventil |
DE102007038124A1 (de) | 2007-08-03 | 2009-02-19 | Südmo Holding GmbH | Doppelsitzventil zur Trennung von Medien |
WO2009090005A1 (de) * | 2008-01-16 | 2009-07-23 | Gea Tuchenhagen Gmbh | Sitzreinigungsfähiges doppelsitzventil |
EP2333385A1 (de) | 2009-12-10 | 2011-06-15 | Alfa Laval Corporate AB | Doppelsitzventil |
FR2956181A1 (fr) * | 2010-02-09 | 2011-08-12 | Defontaine | Dispositif de vanne multivoies pour la circulation de fluides |
JP2012508849A (ja) * | 2008-11-12 | 2012-04-12 | フィッシャー コントロールズ インターナショナル リミテッド ライアビリティー カンパニー | 統合式安全遮断を有する流体バルブ |
US8327881B2 (en) | 2008-09-19 | 2012-12-11 | Spx Corporation | Double seat valve apparatus |
DE102011077717A1 (de) * | 2011-06-17 | 2012-12-20 | Neumo Gmbh + Co. Kg | Doppelsitzventil-Vorrichtung mit Festkörperkontakt |
WO2013185790A1 (de) | 2012-06-16 | 2013-12-19 | Gea Tuchenhagen Gmbh | Sitzreinigungsfähiges doppelsitzventil |
WO2019233932A1 (en) | 2018-06-07 | 2019-12-12 | B.S. Service S.R.L. | Refrigerator appliance with pull-out trolley |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
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DK2203667T3 (da) * | 2007-10-30 | 2012-02-06 | Gea Tuchenhagen Gmbh | Sæderengøringsdygtig dobbeltsædeventil og fremgangsmåde til rengøring af en sæderengøringsdygtig dobbeltsædeventil |
DE202008003976U1 (de) * | 2008-03-20 | 2008-11-27 | Gea Tuchenhagen Gmbh | Sitzreinigungsfähiges Doppelsitzventil mit einer Reinigungseinrichtung für eine Stangendurchführung |
DK200801182A (en) * | 2008-08-28 | 2010-03-01 | Alfa Laval Kolding As | Cleaning system for cleaning a valve seat |
EP2230429A1 (de) | 2009-03-16 | 2010-09-22 | Siemens Aktiengesellschaft | Platzsparendes Regel-Schnellschluss-Ventil für eine Dampfturbine |
JP6169107B2 (ja) * | 2012-02-03 | 2017-07-26 | ゲーエーアー トゥーヘンハーゲン ゲーエムベーハー | 複座弁の座を洗浄するための方法、およびこの方法を実行するための複座弁 |
DE102012003892A1 (de) | 2012-02-28 | 2013-08-29 | Gea Tuchenhagen Gmbh | Verfahren zur Reinigung eines Ventils |
EP2816266B1 (de) * | 2013-06-21 | 2018-04-25 | Alfa Laval Corporate AB | Doppelsitzventil |
US11149869B2 (en) * | 2014-07-07 | 2021-10-19 | Flowserve Management Company | Valve assemblies, valve seats including flexible arms, and related methods |
DE102017007028A1 (de) * | 2017-07-25 | 2019-01-31 | Gea Tuchenhagen Gmbh | Doppelsitzventil mit Membran |
JP7337666B2 (ja) * | 2019-11-07 | 2023-09-04 | 愛三工業株式会社 | 弁装置 |
WO2021148583A1 (de) * | 2020-01-24 | 2021-07-29 | Gea Tuchenhagen Gmbh | Ventil und Verfahren zum Reinigen |
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- 2006-02-18 WO PCT/EP2006/001483 patent/WO2007054131A1/de active Application Filing
- 2006-02-18 AT AT06707068T patent/ATE428879T1/de active
- 2006-02-18 EP EP06707068A patent/EP1945975B1/de active Active
- 2006-02-18 AU AU2006312793A patent/AU2006312793A1/en not_active Abandoned
- 2006-02-18 JP JP2008539265A patent/JP5147706B2/ja active Active
- 2006-02-18 DK DK06707068T patent/DK1945975T3/da active
- 2006-02-18 CA CA 2571244 patent/CA2571244C/en active Active
- 2006-02-18 US US11/659,108 patent/US7905253B2/en active Active
- 2006-04-01 WO PCT/EP2006/002989 patent/WO2007054134A1/de active Application Filing
- 2006-04-01 AT AT06723949T patent/ATE431913T1/de active
- 2006-04-01 EP EP06723949A patent/EP1945976B1/de active Active
- 2006-04-01 US US12/084,789 patent/US7845368B2/en active Active
- 2006-04-01 DK DK06723949T patent/DK1945976T3/da active
- 2006-04-01 AU AU2006312796A patent/AU2006312796B2/en not_active Ceased
- 2006-04-01 CA CA 2626721 patent/CA2626721C/en active Active
- 2006-04-01 DE DE200650003783 patent/DE502006003783D1/de active Active
- 2006-04-01 JP JP2008539266A patent/JP4934673B2/ja active Active
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2009
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EP0174384A1 (de) * | 1984-09-12 | 1986-03-19 | Lavrids Knudsen Maskinfabrik A/S | Doppelsitzventil |
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Cited By (27)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8336572B2 (en) | 2007-06-14 | 2012-12-25 | Gea Tuchenhagen Gmbh | Double seat valve with seat cleaning |
DE102007027464A1 (de) | 2007-06-14 | 2008-12-18 | Tuchenhagen Gmbh | Doppelsitzventil |
DE202007018740U1 (de) | 2007-06-14 | 2009-03-12 | Gea Tuchenhagen Gmbh | Doppelsitzventil |
WO2008151763A1 (de) | 2007-06-14 | 2008-12-18 | Tuchenhagen Gmbh | Sitzreinigungsfähiges doppelsitzventil |
DE102007027765A1 (de) | 2007-06-16 | 2008-12-18 | Tuchenhagen Gmbh | Doppelsitzventil |
DE202007018735U1 (de) | 2007-06-16 | 2009-03-12 | Gea Tuchenhagen Gmbh | Doppelsitzventil |
US8459294B2 (en) | 2007-06-16 | 2013-06-11 | Gea Tuchenhagen Gmbh | Double-seat valve, the seats of which can be cleaned |
DE102007038124A1 (de) | 2007-08-03 | 2009-02-19 | Südmo Holding GmbH | Doppelsitzventil zur Trennung von Medien |
DE102007038124B4 (de) * | 2007-08-03 | 2016-01-21 | Südmo Holding GmbH | Doppelsitzventil zur Trennung von Medien |
US7891376B2 (en) | 2007-08-03 | 2011-02-22 | Südmo Holding GmbH | Double seat valve for separating media |
US8469055B2 (en) | 2008-01-16 | 2013-06-25 | Gea Tuchenhagen Gmbh | Device for driving a double seat valve capable of seat cleaning |
WO2009090005A1 (de) * | 2008-01-16 | 2009-07-23 | Gea Tuchenhagen Gmbh | Sitzreinigungsfähiges doppelsitzventil |
DE102008004597A1 (de) | 2008-01-16 | 2009-07-30 | Gea Tuchenhagen Gmbh | Sitzreinigungsfähiges Doppelsitzventil |
WO2009089853A1 (de) | 2008-01-16 | 2009-07-23 | Gea Tuchenhagen Gmbh | Vorrichtung zum antrieb eines sitzreinigungsfähigen doppelsitzventils |
DE102008004597B4 (de) * | 2008-01-16 | 2017-06-08 | Gea Tuchenhagen Gmbh | Sitzreinigungsfähiges Doppelsitzventil |
US8622076B2 (en) | 2008-01-16 | 2014-01-07 | Gea Tuchenhagen Gmbh | Seat cleaning-capable double-seat valve |
US8327881B2 (en) | 2008-09-19 | 2012-12-11 | Spx Corporation | Double seat valve apparatus |
JP2012508849A (ja) * | 2008-11-12 | 2012-04-12 | フィッシャー コントロールズ インターナショナル リミテッド ライアビリティー カンパニー | 統合式安全遮断を有する流体バルブ |
EP2333385A1 (de) | 2009-12-10 | 2011-06-15 | Alfa Laval Corporate AB | Doppelsitzventil |
EP2357386A1 (de) | 2010-02-09 | 2011-08-17 | Defontaine | Mehrwegventil für Fluidzirkulierung |
FR2956181A1 (fr) * | 2010-02-09 | 2011-08-12 | Defontaine | Dispositif de vanne multivoies pour la circulation de fluides |
US8596302B2 (en) | 2010-02-09 | 2013-12-03 | Definox Sas | Multi-path valve device for fluid circulation |
DE102011077717A1 (de) * | 2011-06-17 | 2012-12-20 | Neumo Gmbh + Co. Kg | Doppelsitzventil-Vorrichtung mit Festkörperkontakt |
DE102011077717B4 (de) * | 2011-06-17 | 2015-05-21 | Neumo Gmbh + Co. Kg | Doppelsitzventil-Vorrichtung mit Festkörperkontakt |
US8950423B2 (en) | 2011-06-17 | 2015-02-10 | Neumo Armaturenfabrik-Apparatebau-Metallgiesserei Gmbh + Co. Kg | Double-seat valve device |
WO2013185790A1 (de) | 2012-06-16 | 2013-12-19 | Gea Tuchenhagen Gmbh | Sitzreinigungsfähiges doppelsitzventil |
WO2019233932A1 (en) | 2018-06-07 | 2019-12-12 | B.S. Service S.R.L. | Refrigerator appliance with pull-out trolley |
Also Published As
Publication number | Publication date |
---|---|
EP1945976B1 (de) | 2009-05-20 |
AU2006312796B2 (en) | 2012-02-02 |
DE502006003783D1 (de) | 2009-07-02 |
AU2006312796A1 (en) | 2007-05-18 |
DE502006003492D1 (de) | 2009-05-28 |
ATE431913T1 (de) | 2009-06-15 |
CA2571244C (en) | 2009-09-15 |
DK1945976T3 (da) | 2009-09-07 |
DK1945975T3 (da) | 2009-08-31 |
JP2009515124A (ja) | 2009-04-09 |
EP1945975B1 (de) | 2009-04-15 |
CA2571244A1 (en) | 2007-05-12 |
EP1945976A1 (de) | 2008-07-23 |
WO2007054134A1 (de) | 2007-05-18 |
JP2009515125A (ja) | 2009-04-09 |
US20090008594A1 (en) | 2009-01-08 |
US7905253B2 (en) | 2011-03-15 |
CA2626721C (en) | 2013-06-18 |
JP5147706B2 (ja) | 2013-02-20 |
HK1125990A1 (en) | 2009-08-21 |
US20090044874A1 (en) | 2009-02-19 |
US7845368B2 (en) | 2010-12-07 |
AU2006312793A1 (en) | 2007-05-18 |
ATE428879T1 (de) | 2009-05-15 |
EP1945975A1 (de) | 2008-07-23 |
JP4934673B2 (ja) | 2012-05-16 |
CA2626721A1 (en) | 2007-05-18 |
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