WO1997039266A1 - Doppelsitzventil mit einem gesteuerten leckageraum - Google Patents
Doppelsitzventil mit einem gesteuerten leckageraum Download PDFInfo
- Publication number
- WO1997039266A1 WO1997039266A1 PCT/EP1997/001049 EP9701049W WO9739266A1 WO 1997039266 A1 WO1997039266 A1 WO 1997039266A1 EP 9701049 W EP9701049 W EP 9701049W WO 9739266 A1 WO9739266 A1 WO 9739266A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- double
- valve
- seat valve
- closing member
- valve housing
- Prior art date
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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
Definitions
- the invention relates to a double-seat valve with a controlled leakage space according to the preamble of claim 1.
- a double seat valve with a controlled leakage space can be found in DE 28 18 787 AI.
- this has a further auxiliary valve disk which can be arranged between the two main valve disks designed as seat disks and can be actuated by a separate control rod independently of the movement of the upper valve disk.
- the leakage space is formed between the two main valve disks and is led to the outside via a leakage liquid line formed in the stem of the lower main valve disk. Since neither the main valve plate nor the auxiliary valve plate are equipped as slides with radially acting sealing means, this known double-seat valve cannot switch without leakage.
- the auxiliary valve disk has the task of preventing the liquid from escaping to the outside through the case drain line when the individual main valve disks are switched through.
- a double seat valve of the generic type is from the
- the latter valve has some properties that at least call into question its practical application. So the closing member between the closed and open position of the valve must perform a relatively large stroke. The total stroke results on the one hand from the necessity that the closing member must cover the two sealing points arranged at a distance in the closed position of the valve and, on the other hand, from a further partial stroke, which in the open position of the valve has a sufficient passage cross section between the closing member and adjacent valve housing ensures. In addition, in the open position of the valve, the relatively large axial extension of the closing member hinders the flow in the valve housing part into which the closing member is driven in its open position becomes.
- the proposed solution makes use of the known closure part, which realizes the two sealing points radially on the outside in cooperation with the valve housing, moreover controls the connection between the leakage space and the interior of the valve housing and, in the open position of the double-seat valve, the interior connects the two valve housing parts to one another via a passage opening provided radially on the inside thereof; however, for the purpose of controlling the connection of the interior spaces of the two valve housing parts, it does not have a closing member which covers both sealing points in the closed position of the double seat valve.
- the closure part in cooperation with the first valve housing part, realizes the first sealing point, and in the closed position, the closing member has the task of forming the second sealing point in cooperation with the second valve housing part.
- the closure part protrudes less into the associated valve housing part by the partial stroke by which it is already immersed in its seating area in the closed position.
- the closing member is in turn reduced to an axial extent, which requires its interaction with the assigned and single seat surface.
- a further closing member is provided, which is designed in the manner of a slide, and which seals in any other than in the open position of the double-seat valve within the passage opening of the closure part is displaced, which comes into sealing contact with the closing element in the course of the opening movement of the double seat valve and is transferred together with this into the open position.
- the first-mentioned closing element can be designed as a seat plate or also as a slide piston
- the second closing element is inevitably a slide piston, so that further advantages can be achieved with the proposed double-seat valve, which are outlined below and which the known valve does not have.
- the second closing element is initially intended to seal off the interior of the valve housing part assigned to this sealing point from the leakage space.
- the second closing element can be moved upwards in the closed position of the valve in such a way that it closes flush with the frontal boundary surface of the closure part which projects into the receiving valve housing part. This avoids the dead space formed in the known valve by the passage opening of the closure part.
- the displacement of the second closing member within the closure part can result in the liquid being removed from the inner lateral surface of the closure part, which forms part of the boundary of the leakage space.
- This stripping process has an especially advantageous effect if, during the closing movement of the double-seat valve, this stripping process is carried out in the opposite direction, as a result of which the inner circumferential surface of the closure part wetted with product during the opening of the valve is stripped almost product-free.
- the double seat valve according to the invention is also fundamentally seat cleanable.
- the closing part or the closing member in the closed position of the double-seat valve, can be displaced into the respectively adjacent valve housing part in such a way that the assigned sealing point is exposed, and that the leakage point is exposed via the sealing point exposed by the partial stroke space is connected to the interior of the associated valve housing part.
- the proposed double-seat valve is not limited to a specific configuration of the first closing element. Basically, it can be designed as a seat plate or as a slide piston. If, as is provided in an advantageous embodiment, the closing member is designed as a slide piston which seals radially together with its sealing point, this results in the closure part being designed as a cylindrical, annular body, as is also proposed , the possibility of designing the outer lateral surface of the closure part and that of the closure member to have the same diameter h the. This embodiment simplifies the entire locking member and locking part configuration. and it also ensures that the surfaces of the closure part and the closing member wetted with product in the area of the sealing points are made sufficiently product-free by the present wiping effect.
- the passage opening of the closure part has at least one passage cross-section corresponding to the nominal cross-section of the double-seat valve.
- the sealing points between the valve housing on the one hand and the closure part or the closing member on the other hand are realized by means of sealing means arranged on the valve housing side or on the closing member or closure part side.
- the sealing configuration is particularly simple if the sealing means are provided on the valve housing side.
- Sealing points as the sealing means for realizing the Ab ⁇ is further proposed to provide either two discrete, separate seals or a one-piece seal.
- the double-seat valve according to the invention creates, in a surprisingly simple manner, favorable conditions for the most extensive implementation of the so-called US 3A standard.
- a further advantageous embodiment of the proposed double-seat valve provides for the leakage space to surround the valve housing on the circumference in a ring-shaped opening that is open at the top or in a self-contained manner ß collecting housing with drain connection is drained.
- the collecting housing is designed to be self-contained and has a further connection, as is also proposed, there is the possibility, if the drain connection for the drainage is still tightly closed in this constellation, the leakage space under negative or positive pressure to be set against the lowest or the highest pressure which acts in one of the two adjacent valve housing parts. If the first pressure condition is met, then no mixing of hostile media can occur if there is negative pressure in one part of the valve housing or in both. If the second printing condition is given, then it is ensured that no if any toxic media occurs in the vicinity of the double seat valve.
- a wiper seal is provided in an end face of the closure part facing the closing element, which is connected to the end face of the closure part Corresponding ring surface of the closing member interacts in such a way that the wiper seal wipes the ring surface in the radial direction from the inside to the outside.
- Another embodiment of the double-seat valve according to the invention provides for an extension of the closing member in its opening direction, in such a way that this extension seals the second valve housing part and penetrates into the vicinity of the double-seat valve.
- This measure reduces the opening force required for the closing element compared to that which is usually under pressure in the medium present in the second valve housing part (so-called balancer solution for the closing member), and it creates the possibility, as is also proposed, of connecting the leakage space to the surroundings of the double-seat valve by means of a further connecting path.
- the double seat valve has a further so-called 'fill port' which instead of the passage cross section between the leakage space and the area around the double seat valve is available between the two valve housing parts.
- Additive solutions of the two connection paths are also possible, each of which can then be emitted smaller than the nominal cross section of the double-seat valve. It can thus be seen that the double-seat valve according to the invention, depending on the requirements and conditions, optionally contains various configurations in this regard.
- the passage cross-section of the connection between the leakage space and the surroundings of the double-seat valve, the so-called leakage outlet can be carried out very simply and in particular in accordance with the requirements of the so-called US 4 3A standard if a separate intermediate housing is provided, which arranged between the valve housing parts, releasably connected to them and if the required passage cross-sections are formed in this intermediate housing, distributed over its circumference.
- This solution allows the use of standardized valve housing parts, since the respective connection XL fertilization with the intermediate housing is done in the same way as the valve housing parts are interconnected.
- the features of the proposed double seat valve that are essential to the invention can also be applied to a so-called double change valve.
- a connection path to the valve housing on one or the other adjacent side is optionally switched from a central valve housing part.
- One of the two valve seats is designed as a double seat with a leakage outlet, while the other has a simple seal.
- This special application is achieved in that an additional closing member is provided coaxially to and at a distance from the closing member and is firmly connected to the latter via a rod extension.
- This additional closing element forms a second sealing point in a second housing opening in the valve housing part receiving the closing element when the closing element assumes its open position, the second housing opening lying opposite the housing opening interacting with the closing element and the connection to a third valve part of the housing.
- This valve like the one mentioned above, is a change-over valve which can be switched alternately from a central valve housing part to one or the other adjacent valve housing part, in which case the two seat areas are designed as double seats with leakage protection.
- valve housing arrangement mirror image of the tube axis of the second valve housing part, with a view of the entire Valve housing arrangement is thus provided for the middle, a further and essentially the same valve housing arrangement, each of these valve housing arrangements being associated with a closing member configuration and a closure part which, in their respective assignment to one another and in relation to the tube axis, are each parallel to ⁇ are arranged one another and all are actuated from the side of the mirror-image supplemented valve housing part.
- FIG. 2 shows a similar cross section through the double seat valve according to FIG. 1 in a first intermediate position, in which the closure part is 'picked up' by the second slide;
- FIG. 2a shows a further cross section through the double seat valve according to FIG. 1 in a subsequent second intermediate position, in which the first closing element is 'picked up' by the second closing element;
- FIG. 3 likewise shows a cross section through the double seat valve according to FIG. 1 in a subsequent third intermediate position, in which the first closing member is substituted by the closure part at the associated sealing point;
- FIG. 4 shows a further cross section through the proposed gene double seat valve according to FIG. 1 in its open position;
- 5 shows a cross section through part of the seat area of the open double-seat valve according to FIG. 1 with a wiper seal arranged in the end face of the closure part; 5a shows the seating area of the double-seat valve according to FIG. 5 in an intermediate position, as can be seen in FIG. 3, the wiper seal being in contact with the closing member;
- Double-seat valve according to the invention with an intermediate housing detachably arranged between the valve housing parts and having a leakage outlet designed according to the American I 3A standard;
- FIG. 6a an advantageous embodiment of the seat
- FIG. 7 shows a view of the double-seat valve with an intermediate housing according to FIG. 6;
- FIG. 8 shows a cross section through a double shuttle valve, in which the features essential to the invention are used;
- FIG. 9 shows a cross section through a double seat valve according to the invention, in the case of different sizes
- Figure 10 shows a double seat valve according to the invention in an arrangement as a tank outlet valve
- FIG. 11 shows the features of the proposed struck double-seat valve in its application to a so-called double D. double change valve.
- a valve housing 1 ( Figure 1) of the double seat valve consists of a first and a second valve housing part la and lb.
- a housing opening 1c is provided, which are arranged with the same diameter and coaxially.
- Each housing opening lc is bordered by a seat ring ld or le, the first seat ring ld forming a first sealing point 7 in cooperation with a closure part 3 and the second seat ring le forming a second sealing point 8 in cooperation with a closing member 2.
- the first sealing point 7 is formed by a sealing means 70 * on the valve housing side, a discrete, separate seal 70, and the second sealing point 8 is formed by a sealing means 80 * likewise arranged on the valve housing side, a similar seal 80 .
- the two sealing points 7 and 8 can also be formed on a one-piece seal 700.
- Both the closure part 3 and the closing member 2 are each designed like a slide and can be moved in translation.
- the outer jacket surfaces of the closure part 3 and the closing member 2 are of the same diameter. It is also possible to design the closing member 2 as a seat plate, the sealing means 80 * or the seal 80 either having to perform an additional axial sealing function or providing a further seal which realizes the seat seal of the closing member 2.
- the closure part 3 is designed as a cylindrical, ring-shaped body which on the inside has a passage opening 3b in which a two-part l6 th closing element 4 is arranged, which is designed in the manner of a slide and which is " sealed in any other position than in the open position of the double-seat valve within the passage opening 3b.
- the second closing element 4 carries a slide seal 9 radially on the outside, which on the one hand, has a radial sealing function with respect to the passage opening 3b and, on the other hand, an axial sealing function when it contacts the end face of the closing element 2.
- the lateral surface of the passage opening 3b, the second closing member 4 and the first closing member 2 delimit a leakage space 5, which has an annular passage cross-section 5a, which only connects the valve housing parts la and lb via a plurality of connecting webs lf distributed over the circumference connects to each other, is connected to the surroundings of the double seat valve.
- the second closing member 2 is connected to a rod 2 a, which is led out of the first valve housing part 1 a through a housing bushing lg in the upper side and into a drive 6.
- a rod 2 a Stored on the rod 2a and inserted into the drive 6 in the same way is an inner hollow rod 4a which carries the second closing member 4 at its lower end.
- An outer hollow rod 3a is connected to the closure part 3 via webs 3f; it surrounds the inner hollow rod 4a, is mounted thereon and also guided into the drive 6.
- the upper end face of the second closing member 4 is flush with the end face of the closure part 3 facing the drive 6, so that in the closed position shown, no puddle or dead space is formed in this area of the closure part 3.
- the axial spacing between the closure part 3 and the second closing element 4 takes place via a recess 4d formed on the latter in the region of the transition between the closing element 4 and its hollow rod 4a.
- the annular gap between the outer and inner hollow rods 3a and 4a is closed in the recess 4d by a hollow rod seal 10.
- the outer hollow rod 3a is sealed in the housing bushing lg via a rod seal 11.
- An annular gap 14 between the rod 2a and the inner hollow rod 4a opens into the leakage space 5 and can be used as a feed path for cleaning and / or disinfectants to the leakage space 5 serve from outside.
- FIG. 1 first showing, by way of example, a possible form of drive with which the individual lifting movements required for the switching process can be implemented.
- a drive piston 6a is provided in the drive 6, which is sealed by an outer piston seal 6g in the drive housing (not specified in any more detail) and which is acted upon by a prestressed main spring 6c which is supported against the lower end face of the drive housing.
- the drive piston 6a is connected via a hollow rod head 4b to the inner hollow rod 4a and is penetrated on the inside by the rod 2a. The penetration point is sealed by an inner piston seal 6h.
- a rod head 2b is provided, on which a spring abutment 2c is formed Is 1%.
- a fourth spring 6f is supported on the latter, which, on the other hand, is in contact with the drive piston 6a.
- the rod head 2b bears against the upper front-side boundary surface of the drive housing, as a result of which the upper end position and thus the closed position of the closing member 2 are clearly defined at the same time.
- the rod end 2b has a recess 2d at its lower end, at which the drive piston 6a finds its upper end position.
- the upper end position of the drive piston 6a inevitably also defines the upper end position of the second closing element 4 and, via its recess 4d, as far as it relates to the closed position of the double-seat valve shown in FIG. 1, the lower end position of the closure part 3.
- a displacement of the closure part 3 upwards is ensured in the closed position shown by a stop (not shown) in the area between the lower frontal boundary surface of the drive housing and the housing lead-through lg.
- the outer hollow rod 3a is provided at its upper end with a hollow rod head 3d, on the end of which a spring abutment 3c is formed for a second spring 6d, which on the other hand is supported against the lower end-side boundary surface of the drive housing.
- a recess 3e is provided, via which the lower end position of the closure part 3 is defined in the open position of the double seat valve (see FIG. 4).
- a driving plate 6b is supported on the latter, which acts as a spring abutment for a preloaded third spring 6e, which is supported on the other hand on the drive piston 6a serves.
- the drive plate 6b is axially spaced from the spring abutment 3c on the hollow rod head 3d, by means of which the axial displacement movement of the second closing member 4 within the passage opening 3b in the first intermediate position (see FIG. 2) is determined.
- the axial distance between the drive plate 6b and a recess 4c on the hollow rod head 4b (FIG. 1) ultimately determines the passage cross section between the second closing member 4 and the second seat ring le in the second valve housing part 1b in the open position of the double seat valve (see FIG. 4) .
- a pressure medium connection 6i introduces pressure medium D into the drive 6 in order to act on the drive piston 6a.
- the space below the drive piston 6a is vented or vented via a second pressure medium connection 6k (L2 or LI).
- this pressure medium can be used to supply D1, so that, in addition to the pretensioning force of the main spring 6c, an additional force can be impressed on the drive piston 6a.
- This additional force can ensure that any pressure surges that may occur in the first valve housing part 1 a do not lead to a displacement of the second closing member 4 within the passage opening 3 b (blocking measure).
- a guide ring 12 through which the outer hollow rod 3a is guided through the lower end face of the drive housing, is additionally to be provided with a sealing function.
- FIG. 2 a first significant intermediate position is reached when the closure part 3 is 'picked up' by the second closing element 4.
- the drive piston 6a is shifted downwards until the drive plate 6b comes to rest on the hollow rod head 3d.
- the second closing member 4 is shifted so far downward in the passage opening 3b that it is flush with the lower end face of the closure part 3.
- the further intermediate position shown in FIG. 2a is characterized by the pick-up position of the first closing member 2 by the second closing member 4.
- the first and second closing elements 2 and 4 are located are in sealing contact with one another via the slide seal 9.
- the first closing member 2 is position 8 (seal 80) is substituted by the closure part 3.
- the hollow rod head 3d has come into contact with its recess 3e on the lower end face of the drive housing.
- the closure part 3 has thus reached its lower end position.
- it forms the sealing points 7 and 8 (seals 70 and 80).
- the first closing member 2 has not yet detached from the lower end face of the closure part 3, and the second closing member 4 is still at the lower end of the passage opening 3b.
- the double seat valve then opens.
- the opening movement is ended when the recess 4c of the hollow rod head 4b has come into contact with the drive plate 6b (FIG. 4). Now there is a passage of fluid F between the interior of the first valve housing part la and that of the second valve housing part lb.
- the drive piston 6a, the hollow rod head 4b, the driving plate 6b and the hollow rod head 3d are locked together and are in their respective lower end positions.
- a wiper seal 13 is provided, which in the closing process of the double seat valve cooperates with an annular surface 2 * of the closure member 2 (FIG. 5a) corresponding to the end face of the closure part 3 that the wiper seal 13 contacts the ring surface 2 * in the radial direction from the inside to the wiper.
- Product that is in the open position of the double seat valve wetted the ring surface 2 *, stripped during the closing process.
- FIG. 1 another embodiment of the closing element 2 is indicated by dash-dotted lines, the closing element 2 being longer in its opening direction and thereby penetrating the second valve housing part 1b in a sealed manner into the surroundings of the double-seat valve.
- the extension 2e has in the area of its sealed penetration through the second valve housing part 1b the same or approximately the same diameter as the closing member 2 in the area of its sealing point 8, and it is also designed as a tube that connects a connection path 2g between the leakage space 5 and the area around the double seat valve.
- the passage opening 2f of the tube is expediently designed with a passage cross section corresponding to the nominal cross section of the double seat valve. This configuration creates a so-called 'fill port' which can be used instead of the passage cross section 5a between the valve housing parts la and lb. Additive solutions from the two connecting paths 5a and 2g are also possible.
- the leakage space 5 has between the first and the second valve housing parts la and lb a free passage cross section 5a which is only interrupted by the connecting webs 3f and which, due to the freely selectable distance between the two valve housing parts la and lb, at least can be designed as large as the nominal cross-section of the largest valve connecting piece.
- the proposed double seat valve is the
- the first closing member 2 cannot be pressed open in the event of overpressure or pressure surges. Before the second closing member 4 is pressed on, it must first measure its entire displacement within the closure part 3; only then does leakage occur. This situation ensures sufficient safety in the event of pressure surges.
- a mechanical lock in the drive 6 can prevent the press-on when the overpressure persists.
- an additional pressurization with pressure medium D1 is provided on the underside of the drive piston 6a.
- the proposed double seat valve according to the invention can be installed in a wide variety of positions. It can range from 'standing' to 'lying' (tilted 90 °) to 'overhead'
- the main spring 6c (see e.g. FIG. 1) is arranged in the drive 6 in such a way that it keeps the double seat valve in the closed emergency position in the event of a power failure.
- the second spring 6d fixes the closure part 3 in its upper end position when the second closing member 4 executes its displacement movement within the passage opening 3b from top to bottom.
- the third spring 6e presses the closure part 3 downward (it is made stronger than the second spring 6d) when the second closure element 4 moves together with the closure part 3 in the direction of the first closure element 2 (see FIGS. 2 and 2a).
- the fourth spring 6f holds the first closing element 2 in its closed position within the second seat seal 80 until the second closing element 4 has moved against the first closing element 2 and presses both closing elements 2 and 4 together when the double-seat valve is open is (see Figures 2 to 4).
- FIG. 6 shows an intermediate housing lz releasably connecting the first and second valve housing parts la and lb to one another and receiving the leakage outlet 5a.
- the valve housing parts la and lb as well as the intermediate housing lz are made with flanges (not described in more detail) - Equipped, which are connected to one another via so-called tension rings.
- one of the valve housing parts la, lz and lb, lz can seal against one another e &
- FIG. 7 The view (FIG. 7) of the double seat valve shown in section in FIG. 6 with a separate intermediate housing lz clearly illustrates on the one hand the proportions of the leakage outlet 5a when it is designed and operated under the conditions of the US '3A standard'. on the other hand, it shows impressively that the critical area of the double-seat valve can be directly inspected and inspected via the leakage outlet 5a of the intermediate housing lz.
- valve housing part la * below the second valve housing part 1b. Both valve housing parts lb and la * are connected to one another via a second housing opening lc *, which lies opposite the housing opening lc interacting with the closing element 2.
- An additional closing member 2 * is provided coaxially with and at a distance from the closing member 2 and is firmly connected to it via a rod extension 2a *, which forms a second sealing point 8 * with the second housing opening 1c * when the closing member 2 assumes its open position .
- the closing element arrangement 2, 2 * can be switched alternately such that either the flow path F to the first valve housing part 1 a or that to the third valve housing part 1 a * is open from the central valve housing part 1 b.
- the closed position of the closing member 2 and that of the closure part 3 are leakage-protected (leakage outlet 5a) via the intermediate housing 1z.
- the simple sealing point 8 * is realized between the middle valve housing part 1b and the third valve housing part la *.
- the arrangement of the intermediate housing lz also enables a combination of different nominal diameters D1 and D2 of the valve housing parts la and lb connected to one another via the intermediate housing lz.
- the passage cross section required in the double seat area is realized in the intermediate housing lz; it is not subject to any restrictions due to the larger diameter D2 of the second valve housing part 1b.
- valve housing parts la and la * are provided on both sides of the central valve housing part 1b, each with the interposition of an intermediate housing lz or lz *, in a mirror-image arrangement.
- the closing element and closing part configurations 2, 4, 3 or 2 *, 4 *, 3 * respectively assigned to the valve housings la and la * in connection with the intermediate housing lz or lz * are arranged in a double arrangement, parallel to one another, are provided and the closing members 2, 4 or 2 *, 4 * and the closing parts 3 or 3 * are actuated from the side of the third valve housing part which is supplemented by a mirror image.
- the connecting path F between the middle housing part 1b and the third valve housing part la * is open.
- the dot-dash line shows the position of the closing members 2, 4 or 2 *, 4 * and the closure parts 3 or 3 * when the connection to the first valve housing part 1 a is open.
- the end positions of the locking elements and locking parts are each marked with a 'dash' (eg locking element 2: end position 2 '; locking part 3 *: end position 3 *').
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding Valves (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP97914184A EP0891506A1 (de) | 1996-04-13 | 1997-03-03 | Doppelsitzventil mit einem gesteuerten leckageraum |
AU21530/97A AU2153097A (en) | 1996-04-13 | 1997-03-03 | Double-seated valve with a controlled leakage space |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19614648 | 1996-04-13 | ||
DE19614648.8 | 1996-04-13 | ||
DE19618235A DE19618235C1 (de) | 1996-04-13 | 1996-05-07 | Doppelsitzventil mit einem gesteuerten Leckageraum |
DE19618235.2 | 1996-05-07 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997039266A1 true WO1997039266A1 (de) | 1997-10-23 |
Family
ID=26024717
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1997/001049 WO1997039266A1 (de) | 1996-04-13 | 1997-03-03 | Doppelsitzventil mit einem gesteuerten leckageraum |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0891506A1 (de) |
AU (1) | AU2153097A (de) |
WO (1) | WO1997039266A1 (de) |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3042887A1 (de) * | 1979-11-20 | 1981-06-04 | Erik Haakan Olaf Staffanstorp Jeppsson | Ventil |
EP0140432A2 (de) * | 1983-10-06 | 1985-05-08 | Appendagefabriek "Hoogeveen" B.V. | Absperrventil |
US4605035A (en) * | 1984-09-14 | 1986-08-12 | Lavrids Knudsen Maskinefabrik A/S | Double seat valve |
-
1997
- 1997-03-03 EP EP97914184A patent/EP0891506A1/de not_active Withdrawn
- 1997-03-03 AU AU21530/97A patent/AU2153097A/en not_active Abandoned
- 1997-03-03 WO PCT/EP1997/001049 patent/WO1997039266A1/de not_active Application Discontinuation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3042887A1 (de) * | 1979-11-20 | 1981-06-04 | Erik Haakan Olaf Staffanstorp Jeppsson | Ventil |
EP0140432A2 (de) * | 1983-10-06 | 1985-05-08 | Appendagefabriek "Hoogeveen" B.V. | Absperrventil |
US4605035A (en) * | 1984-09-14 | 1986-08-12 | Lavrids Knudsen Maskinefabrik A/S | Double seat valve |
Also Published As
Publication number | Publication date |
---|---|
EP0891506A1 (de) | 1999-01-20 |
AU2153097A (en) | 1997-11-07 |
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