WO1997039265A1

WO1997039265A1 - Double-seated leak-sealed flap valve

Info

Publication number: WO1997039265A1
Application number: PCT/EP1997/001240
Authority: WO
Inventors: Peter Mette
Original assignee: Peter Mette
Priority date: 1996-04-13
Filing date: 1997-03-12
Publication date: 1997-10-23
Also published as: EP0891505A1; AU2026297A

Abstract

The invention relates to a double-seated flap valve, especially as a blocking component in pipes securely to separate hostile fluids, especially for the food and beverages industry, as described in the preamble to claim 1, which operates with little or no leakage and where the leakage chamber can easily be cleaned in both the closed and open positions. This is achieved in that, during opening, the flaps (2) are moved from their closed position while maintaining a seal at their sealing points (2a) fitted at the periphery against the inner wall of a central housing section (1a; 9) initially coaxially with the pipe and in opposite directions until they form a unit (2, 2; 2, 5, 2) accepting the leakage chamber (16) which is rotatably fitted directly or indirectly in the housing section (1a) via two coaxial spindle pins (5a) arranged on opposite sides of the unit (2, 2; 2, 5, 2) and taken into the open position via this bearing.

Description

Double seat flap valve with leakage protection

The invention relates to a double-seat flap valve with leakage protection, in particular as a shut-off device in pipelines for the safe separation of hostile fluids, in particular for the food and beverage industry, according to the preamble of claim 1.

A double seat flap valve with leakage protection of the generic type is known from DE 2948534 A1. It has a leakage space between the two shut-off devices, from which any leaks due to seal wear or pressure surge or as a result of foreign bodies can be discharged to the outside without pressure. In principle, the valve consists of two independent flap valves, the two similar shut-off elements being driven simultaneously by a single drive. The leakage space has a flushing and a leakage outlet, both of which are forcibly actuated via an associated closing element depending on the position of the shut-off organs. In the open position of the flap valve, both outlets are closed while they are open in the closed position of the valve .

A double seat flap valve which is identical to the aforementioned known valve with regard to the arrangement of its flaps and the arrangements for its actuation has already been described in DE 2847038 A1. In contrast to the valve according to DE 2948534 A1, here are the connection paths between the leakage space and the surroundings of the

The valve is not arranged in the housing between the shut-off elements, but predominantly in the spigot of the shut-off elements which is mounted in the housing and is passed through it, and its through openings are forcedly controlled depending on the position of the valve by means of rotary slide-type pinning means.

The two double seat flap valves mentioned have a number of disadvantages. On the one hand, they are relatively large because, in principle, they house two flap valves, the shut-off elements of which must be spaced from each other in such a way that they do not interfere with their movement during the closing or opening movement or the product flow in the open position restrict inappropriately. In addition, relatively complex measures must be taken so that the two openings of the leakage space can be controlled as a function of the switching movement of the double-seat flap valve. Each of the two flaps has two shaft journals, each of which must be mounted in the housing and also sealed there. For the simultaneous actuation of the shut-off devices, mechanical pre- take steps so that the necessary actuating movement can be transferred to the shut-off devices via a single drive.

DE 2821 766 A1 or US 21 19816 each describe a double-seat flap valve in which the two flaps belonging to the clamping unit, in addition to an axis for pivoting movement about an axis arranged transversely to the pipeline, also perform an opposing displacement movement coaxial to the axis of the pipeline ¬ lead. The two flaps are initially moved out of their closed position during the opening process in the above sense, in order then to be pivoted in their approximated position into the open position of the double-seat flap valve. This sequence of movements permits a construction of the valve which is considerably more space-saving than the two known valves mentioned at the beginning (DE 2948 534 A1, DE 2847 038 A1).

The known valve according to DE 2948534 A1 or DE 2847 038 A1 has the disadvantage with regard to the realizable sealing forces that each flap valve of the given basic type has, namely that the sealing forces are determined by the degree of radial preload between the seal and the shut-off device in its closed position. As a result of the limited sealing forces, the product pressures that can be applied to the closed shut-off devices are limited. In contrast, in the double-seat flap valve known from DE 2821 766 A1 or US 21 19816, the two flaps can be pressed by their drive mechanism with their displacement movement, which is oriented coaxially to the axis of the pipeline, with a sealing force which presses against the respectively assigned seat surface is determined only by the dimensioning of the drive elements and the provision of sufficiently large drive forces.

In the double-seat flap valve according to US 21 19816, the two flaps are designed in such a way that in the open position of the valve they delimit an interior space which is closed off between them, but which has no connection to the outside. Therefore, in the open position, this interior space can neither be drained into the open, nor can it be cleaned in the flow in this position, for example in order to clean off impurities due to sealing defects. However, cleaning in this regard is necessary if such a valve would be used in the food or beverage industry, since during the opening and closing movement of the valve, the product flowing in it and the ones that delimit the interior Surfaces come into contact. Contamination and contamination of these surfaces then leads to the product being recontaminated.

In the closed position, the double-seat flap valve according to DE 2821 766 A1 forms an interior between the two flaps, which can be connected to the surroundings of the valve via at least one line. As a result, in this position the indication and possibly the removal of leakage and also a possibility of flushing the interior is given, however, such a configuration requires the arrangement of additional control elements which switch the connection paths to this interior. In the open position of the double-seat flap valve, the two flaps do not form a self-contained space, so that in this position neither a leakage indicator nor a purging of the valve in this area is possible.

DE-GM 71 12601 describes a double-seat flap valve in which a closing body essentially consists of an inner body and at least one plate that can be pressed onto the seat surface. The inner body has two passages intersecting at right angles and is mounted in the spherical housing via at least one hollow cylindrical pivot axis engaging one of the passages. The pressing plate is guided on the inner body in the longitudinal direction of the passage so as to be displaceable perpendicularly to the pivot axis, and a switching and locking means is provided on the plate and on the inner body, by means of which the position of the closing body and the Plate in the housing is adjustable. Compared to the double-seat flap valve according to DE 2821 766 A1 or US 21 19816, this valve differs in that the two flaps maintain their sealing effect on the way from their closed to the open position with respect to an assigned middle housing part, the final body. The interior in this final body is connected to its surroundings both in the closed and in the open position of the valve, so that leak detection and flushing is possible in each of these positions, but in the closed position of the valve between its housing and the final body formed a further interior, which must be connected to the environment via controllable connections so that the considerable switching leakage accumulating in this area when the valve closes can be dissipated. In the course of opening the valve, these connections must be closed by external switching devices. Such a double-seat flap valve is completely unsuitable for use in particular in the food and beverage industry due to the switching leakage that is present DE 24 35 125 A1 describes a shut-off flap with a housing and a closure flap which can be swiveled by ninety degrees from an open position into a closed position, the latter consisting of two valve disks which are arranged symmetrically on both sides of the swivel axis and can be driven in this manner are that their distance from each other is changeable. The valve disks cooperate with seats provided in the housing in such a way that an increase in their distance in the closed position causes each valve disk to be seated against the associated seat. In the case of extreme demands on the sealing effect, according to a proposed embodiment, the possibility is given to evacuate the space between the flap disks depending on the specific application or to apply excess pressure or to fill them with a barrier medium. Although the space between the flap disks can be spooled both in the closed position and in the open position of the valve and also draimeΦar (Fig. 4), if this is arranged appropriately for this space, this valve also does not leave little leakage and certainly not do not switch leakage-free, since the two flaps belonging to the shooting unit, which during the opening process are initially shifted from their closed position coaxially to the axis of the pipeline and in opposite directions to each other, during the opening process from the closed position a sealing effect of their sealing points on the circumference against the housing. Do not maintain the inner wall, but temporarily give up this sealing effect until they come into contact with a central swivel body and form a closed clamping unit in this position

The flap valves described in DE 29 48 534 A1 or DE 2847 038 A1 also have considerable switching leaks (in particular during the closing process), since the fluid trapped between the shut-off devices is discharged into the surroundings of the valve. During the opening process, they only switch to low-leakage if it is possible to control the two leakage openings and close them completely on the short twisting path of the shut-off element between its closing position and an intermediate position in which it is just closing. If this does not succeed, overlaps of the switching movements for the shut-off devices and the switching elements provided for controlling the leakage space openings are necessary, which has the consequence that switching leakages occur. Finally, it should be noted that with these valves too, the leakage space is only in the The closed position of the valve can be cleaned since it does not exist in the open position of the valve.

In the case of the double-seat flap valves described above, the arrangement of the shut-off elements and the leakage space openings in connection with the assigned control elements also does not allow the leakage process to be as large as possible, as is often required today, ideally with a passage cross-section that suits this Nominal cross section of the largest pipe connected to the valve corresponds. In the event of seal defects and the associated leakages, if the leakage drain cross-section is too small, there is a risk of an impermissible pressure build-up in the

Leakage cavity, since the leakage quantities cannot be discharged without pressure or almost without pressure via the narrow drain cross-section.

The absolutely pressure-free removal of leakage quantities from the leakage space is a requirement that has recently become increasingly important, particularly on the US market or in the US sphere of influence, when using double-seat valves in dairy technology. This is to meet the requirements of the US 'SA standard', which states that the leakage space should be connected to the atmosphere in a drainable manner with a cross-section corresponding to the nominal diameter of the largest pipe connected to the valve.

The present invention has for its object to provide a double-seat flap valve with leakage protection of the generic type that switches low leakage or leakage¬ and whose leakage space is easy to clean both in the closed and in the open position.

The object is achieved by a double-seat flap valve with the features of claim 1, while advantageous embodiments of the proposed double-seat valve valve are the subject of further subclaims.

In contrast to the known double-seat flap valves of the generic type, in the solution according to the invention the two flaps are initially coaxial with the axis while the sealing parts arranged on the circumference are kept sealed against the inner wall of an associated middle housing part of the pipeline and mutually displaced. This makes it possible to have an almost leak-free movement realize. As soon as the two flaps are approached from their closed position during the opening process in such a way that they form a unit which accommodates the leakage space and is closed off from the adjacent interior spaces of the valve, the entire unit, which has two coaxial, on opposite sides of the Unit arranged shaft journal is rotatably mounted directly or indirectly in the housing part, can be moved to this position in the open position overall. Since on the one hand the leakage space remains closed in the open position, no product can enter it from the environment inside the valve, on the other hand it is possible to clean it also in the open position of the valve by supplying cleaning agent from the surroundings of the valve.

According to a first embodiment of the proposed double-seat flap valve, the unit consists only of the two flaps, each of which comes into abutment against one another at the circumference and thereby seals, and in this position absorb and limit all the leakage space.

According to a second embodiment of the proposed double-seat flap valve, it is provided that the unit consists of the two flaps and a support arranged between them. The unit which accommodates and delimits the leakage space comes into being when the flaps come into abutment via their sealing parts on their circumference on the support arranged between the flaps, on both sides of this and in each case sealing all around.

In addition, the pressure forces in the product, provided they are above the ambient pressure, ensure that the flaps are sufficiently pressed against one another or against the support so that the leakage space is reliably sealed off from the product when the valve is open. The aforementioned pressure forces thus represent an additional factor usable closing force, the two flaps are caused by closing forces, which are provided by the existing Antπeb, pressed against each other or respectively on the support.

In order to make the bearing points of the Weil pegs cleanable, it is proposed with regard to the unit consisting essentially of the two flaps that the leakage space between the flaps is limited in the course of the opening or closing process and in the open position of the valve in that the flaps predominantly seal each other over these sealing points and that the wave tap in the area of these crossing or tangent sealing points, where they are enclosed in a ring-shaped sealing manner by sealing points which are adapted in their shape to the shaft journal.

With regard to the unit consisting of the flaps and the support ring, with regard to the aforementioned cleaning problems, the shaft journals are provided in the course of the opening or closing process and in the open position of the valve, in the area of the sealing points crossing or tangent, there through in their shape Correspondingly adapted sealing points are encircled in a ring-shaped sealing manner.

In the case of the two aforementioned design variants, in the closed position of the double-seat flap valve, when the flaps are moved apart and pressed onto their seat surfaces, the shaft journal area previously enclosed in an annularly sealed manner by the sealing points in this area is exposed within the closed leakage space and it can cleaned in this position of the valve and sterilized if necessary.

In order to accomplish the ring-shaped encirclement of the shaft journals by the sealing points very simply and without substantial consideration of the circular contour of the sealing points in the peripheral region of the flaps, it has proven advantageous in the second embodiment to have the support ring in the region of its transition to the respective one To provide shaft journals with an annular recess which extends concentrically to the latter and engages in the support ring, into which in the course of the opening or closing process and in the open position, perpendicular to

Axis of the shaft journals and from opposite sides, each correspondingly shaped areas of the sealing points, engage completely in a ring-shaped manner.

In order to ensure the outflow of the fluid required for cleaning and / or sterilization from the leakage space via the bearing points in the above-proposed embodiments of the double-seat flap valve with cleanable bearing points of the shaft pins, an advantageous embodiment provides that the two shaft pins each in a shaft bearing in the housing Find recording, the shaft bearings are each provided with longitudinal grooves that pass through the entire shaft bearing fluid permeable. In the closed position of the valve, the proposed solution also has significant advantages over the known state of the art, in particular with regard to the realization of sealing forces between the flap and the housing. Thus, the flaps in their closing division can be controlled in a defined manner against each other to press the assigned seat surfaces in the direction of the axis of the pipeline. The size of the contact pressure is only a question of the design of the valve, so that the valve reliably blocks against higher product pressures than is the case with the known valves

If the leakage space in the open position of the valve has at least one controlled connection to the surroundings of the valve, as is provided according to a further advantageous embodiment, on the one hand leaks can also be determined in this position and, if a second connection path is present, measures for Cleaning, rinsing and, if necessary, disinfection of the leakage space

The flaps can be displaced in the direction of the axis of the pipeline without difficulty such that the flaps guide one another or that they are each guided in or on or on the support or in a food box. This configuration ensures that the flaps do not tilt in their closed position while they are closing or opening, so that the desired leak-free switching is ensured.

The sealing points are in the peripheral area of the flaps. It is envisaged that these sealing points will each be realized by means of flap-side or housing-side sealing means. The sealing means are designed as discrete seals, which are to be provided either in the circumferential area of the flaps or in the sealing area of the housing. Instead of discrete seals, it is also proposed that the sealing means by coating or sheathing the middle housing, in which the flaps are sealed should be realized with a suitable sealing material. In this case, the valve can be designed so that it switches absolutely leak-free. Finally, it is proposed to carry out the flaps or the middle housing part as a whole from a suitable sealing material, which leads to a relatively simple and therefore inexpensive valve The switching movement of the valve takes place, as is further proposed according to an advantageous embodiment, causally via a single actuator, in a first preferred embodiment of the actuator the displacement movement of the two flaps via a combination of a double-acting toothed rack, which is located on both sides in the Engagement with a gear is located, and a threaded spindle / nut system arranged in each gear is realized. The gearwheels are coaxially drilled through and the respective bore has two nut threads with opposite pitch one behind the other, spaced apart from one another in the center of the gearwheel by a circumferential groove-shaped recess. The sliding movement of the rack causes the two gears to rotate in opposite directions, each of which, in conjunction with the threaded spindle / nut system, produces the opposite translatory sliding movement of the flaps. The entire unit, consisting of the two flaps and the gear serving to translate the two flaps, is rotatably mounted in the valve housing via shaft pins arranged on both sides of a food box; the required rotary movement is also provided via the Antπeb.

In a second preferred embodiment, the drive provides a pressure medium with which the displacement movement of the flaps in the direction of the axis of the pipeline is effected on the basis of a pressure medium-operated second drive arranged between the flaps. In this case, the elements of the second drive can also take over the guidance of the flaps mentioned at the beginning.

In a third preferred embodiment it is provided that the actuator provides a rotary movement by means of an actuator, with which a knee-like arrangement is actuated to generate the sliding movement of the flaps in the direction of the axis of the pipeline. Such a knee-like arrangement also has the advantage that the flaps, particularly in their closed position, are locked so that they can also withstand greater pressure forces or impacts.

Leakage discharge cross-sections that meet the condition of the US 3A standard can be achieved, as is also provided, in that the leakage openings distributed over the circumference of the central housing part are controlled by means of two axial slides. A seat is formed in each of these sleeve-shaped axial slides and two such axial slides are arranged in the central housing part and are each pre-stressed by means of a spring coaxial to the axis of the Piping slidably and sealed against the middle part of the housing. The two springs press the axial slide on each other at their mutually facing end faces by means of two leakage-side seals, while the flaps on their axial displacement into their closed position press the two axial slides apart over the assigned seat surfaces and thereby release the leakage openings mentioned above. This configuration is special Suitable way to meet the so-called 3A requirement and thus to design the leakage outlet in the form of a so-called 'fill port

When the valve closes, hydraulic problems can occur during the translational displacement of the two flap halves, if the medium to be displaced cannot leak through an open end of the pipeline when switching without leakage. This is the case, for example, when the proposed double valve flap valve is used as a shut-off valve of a tank and a shut-off valve is provided in the pipeline on the side of the flap valve facing away from the tank. If this shut-off valve is closed, the flap adjacent to this valve cannot be moved in the direction of the closed shut-off valve in any case if the medium present is incompressed. In this case, it is provided that the housing be used without restriction to ensure the use of the double-seat flap valve -Inside wall of the middle housing part has at least one compensating bore, which, on the one hand, fills out into the interior of the middle housing via a first opening and, on the other hand, a second opening near the respective seat surface

Embodiments of the invention are shown in the drawing and are briefly explained below in terms of structure and function. 1, 1a show a preferred first embodiment of the proposed double-seat flap valve, the flaps being shown in view and the flap shown on the right (FIG. 1) being in its closed position and the flap shown on the left (FIG. 1a) being in its position at the beginning shows the opening or closing movement; 2.2a shows a central section (corresponding to the section shown in FIG. 2b with CC) through a second embodiment of the double-seat flap valve with a support in a plane perpendicular to the axis of the drive shaft, the valve in its closed position (FIG. 2) shown and FIG. 2a also shows the double-seat flap valve in the closed position, the flaps coming into contact with the support; 1 b, 1 c a middle section (corresponding to the section marked with DD in FIG. 1 d) through a double-seat flap valve according to the first embodiment, a displacement antenna being provided between the flaps in a preferred first embodiment and the flaps one on the one hand in their closed position (FIG. 1b) and on the other hand at the beginning of the opening or closing movement (FIG. 1c); 1d shows a central section through the displacement drive according to FIGS. 1b, 1c in accordance with the section profile identified there by AA;

2b shows a central section through the support and its adjacent components in accordance with a section profile marked BB in FIGS. 2, 2a; 3 shows a preferred embodiment of a shaft bearing shown in FIG. 2b with fluid-permeable longitudinal grooves; 2c shows a further central section (C'-C ') through the double-seat flap valve of the second embodiment in accordance with the section profile marked CC in FIG. 2b, the unit formed in contrast to the position of the valve in FIGS. 2 and 2a two flaps and the support ring, is in the open position of the valve; 4,4a is a central section through a third embodiment of the proposed double-seat flap valve in a plane perpendicular to the drive shaft, this embodiment having two axial slides and FIG. 4 the closed valve on one side and FIG. 4a the likewise still closed one, which is at the beginning of the opening movement Valve shows, while the dashed representation of the flap and the support ring shows the full open position; 5 shows the application of the proposed double-seat flap valve in its second embodiment as a connecting member between two cross-directed pipelines; 2d shows a part of the double-seat flap valve in its second embodiment with a central housing part, which is made entirely of a suitable sealing material; 4b, 4c the proposed double-seat flap valve in its third embodiment, the two axial slides being encased with a suitable sealing material and FIG. 4b the closed position and FIG. 4c the loading At the beginning of the opening movement and, in the broken line, the opening division of the valve clarifies and Fig ß a detail in the area of the middle housing part for the purpose of

Realization of switching movements of the flaps under the influence of incompressible media.

The proposed double-seat flap valve in a first embodiment (FIGS. 1 and 1a) consists of a housing 1, which is essentially constructed from a central housing part 1a and the two end-side housing parts 1b. Two disk-shaped flaps 2, preferably circular, are oriented in their respective closing division in two mutually parallel planes transverse to the axis of the pipeline. They each seal by means of a sealing point 2a in their peripheral region against a seat 1d (FIG. 1) of the valve (closing and end position). In the present case, the sealing point 2a is designed as a discrete flap-side seal. A leakage space 16 is provided between the flaps 2. Figure 1a shows the position of the flap 2 at the beginning of the opening or closing movement. In the course of the two last-mentioned movements, the flaps 2 rotate in the shaft journal 5a. The translatory displacement movement of the flaps 2 is effected via a drive rod 3 which is guided coaxially in the shaft journal 5a.

FIGS. 1b, 1c and 1d disclose the configuration of a preferred sliding drive for the translational movement of the flaps 2 when applied to an embodiment according to FIGS. 1,1a. FIG. 1b shows the flap 2 in its closed position, while FIG. 1c documents the position of the flap 2 at the beginning of the opening or closing movement. Figure 1 d discloses a central section through the arrangement according to the Schntttveriauf A-A identified in Figures 1b and 1c. The middle section shown in FIGS. 1b and 1c results from the course of the section marked D-D in FIG. 1d. For a better understanding of the displacement drive, the aforementioned figures are considered in the following in a synopsis.

A drive 7 (not shown) (FIG. 1d) drives a drive rod 3 which can be displaced translationally within the shaft journals 5a and which is designed as a double-acting toothed rack 3b between the two shaft journals 5a. Each of the toothings of the toothed rack 3b is in engagement with a toothed wheel 3c, 3d arranged between the two flaps 2, each of which is coaxially pierced. In each of these holes are one behind the other, in the middle of the gear 3c, 3d by a circumferential groove-shaped

CORRECTED SHEET (RULE 91) ISA / EP Recess 3g spaced from each other, two nut threads with opposing pitch provided (Figures 1b, 1c). The threaded bolts 3e and 3e 'are located in the gearwheel 3c in the assigned nut threads, and the threaded bolts 3f and 3f are screwed into the gearwheel 3d in the respective nut threads. The ends of the threaded bolts 3e and 3f protruding from the toothed wheels 3c and 3d are fastened to the flap 2 shown on the right-hand side, while the threaded bolts 3e 'and 3f on the other side are connected to the left-hand flap 2.

The gearwheels 3c and 3d and the toothed rack 3b are accommodated in a food box 5 * which carries the shaft journals 5a, the food box 5 * in the respective penetration range of its four threaded bolts 3e, 3f, 3e 'and 3f with respect to the interior of the housing 1 , 1a are each sealed by a bellows 17 enveloping the respective threaded bolt and sealing the gland box 5 * with the area of the flaps 2 in question. The anti-friction rod 3 is mounted within the shaft journals 5a (see FIG. 1d) arranged on both sides of the receptacle box 5 * in bearings 3ι which are received by a bore 5b in the shaft journals 5a, so that they can be displaced translationally. The entire unit, consisting of the two flaps 2 in connection with the displacement arm inside the food box 5 *, is rotatably supported via the shaft journals 5a within the middle housing part 1a within the required sequence of movements, the bearing being carried out via shaft bearings 6c, 6d , which can be expediently designed in accordance with the embodiment according to FIG. 3. The sealing points 2a of the flaps 2 enclose the shaft journals 5a according to a preferred embodiment, as can be seen from FIGS. 1 and 1a. With regard to the cleanability of the contact surfaces between the shaft journals 5a and the assigned area of the sealing points 2a, reference is made at this point to the following explanations for FIGS. 1, 1a and 2b. The leakage L is discharged via the transverse opening 5c and the leakage hole 5d

A second embodiment of the proposed double-seat flap valve is illustrated in FIGS. 2 and 2a. Between the two flaps 2 there is a support 5, in which a support 3 is mounted, the support 5, for example as shown in FIG. 2b, in turn being rotatably mounted in the middle housing part 1a. The Antπebswelle 3 is connected via a knee-like arrangement, consisting of a shaft-side joint 3a, a second joint G2, a lever 4, a first joint G1 and a flap-side joint part 2b, each with a flap 2. A leakage space 16 is provided between the flaps 2. Figure 2 shows the flap 2 in its closed position (end position), in which it is pressed onto the assigned seat 1d via the sealing point 2a. If the anti-shafts 3 are rotated in the opening Ö direction Ö, then the above-mentioned knee-like arrangement shortens the distance between the axis of the anti-shafts 3 and the first joint G1 and the flap 2 is brought to bear on the support 5, where it seals all the way round (FIG. 1a). For better guidance of the flaps 2 as they move in the direction of the axis of the pipeline, a mutual guidance of the flaps 2 or a guidance of the flaps 2 are provided in or on or on the support 5

FIG. 2b discloses details of the auxiliary shaft mounting and the connection path between the leakage space 16 and the surroundings of the valve. The support 5 has two shaft journals 5a, each of which is rotatably arranged in the central housing part 1a in a passage opening 1c and there on the one hand via a first and, on the other hand, a second shaft bearing 6c or 6d are guided through the central housing part 1a into the surroundings of the valve. The anti-drive shaft 3 is supported in a bore 5b in the shaft journal 5a. The connection path of the leakage space 16 with the surroundings of the valve is provided in the shaft journal 5a lying at the bottom in the installed position of the valve, a transverse opening 5c penetrating through the support 5 from one flap 2 to the other in the axial direction of the shaft journal 5a in a leak hole 5d continues. Thus, any leakage L that may occur can be drained both in the closed (FIG. 2) and in an open position (FIG. 2c) and, if a supply of cleaning and / or rinsing liquid is provided, the leakage space 16 can also be cleaned Anti-friction elements, not shown, can be arranged in a central opening of the support 5

If the sealing points 2a of the flaps 2 in one embodiment are designed according to FIGS. 1 or 1a or 2b, the shaft bearings 6c and 6d (FIG. 2b) of the shaft journals 5a can be designed according to the embodiment according to FIG. 3 (fluid-permeable longitudinal grooves 6e, the reach through the entire shaft bearing 6c or 6d) In the closed position of the double-seat flap valve, the leakage L or the cleaning or stabilizing fluid reaches the surroundings of the valve via the transverse opening 5c and the leakage hole 5d. In addition, in this position, the sealing surfaces between the shaft bearings 6c and 6d and the respective shaft journal 5a can be cleaned and, if necessary, set. In the course of the opening or closing process and in the open position of the double-seat flap valve, the shaft journals 5a are cleaned by cleaned and, if appropriate, stenistered sealing points sealed this area from the environment. Contamination from the environment or from non-rigid seals is thus avoided.

The design of the double-seat flap valve with a support 5 (FIGS. 2, 2a, 2b), in which the bearing points of the shaft journals 5a can be cleaned in the closed position of the valve, is characterized in particular by the fact that the support 5 is in the region of its Transition to the respective shaft journal 5a is provided with a concentric recess 5k extending into the latter and engaging in the support 5, in the course of the opening or closing process and in the open position, perpendicular to the axis of the shaft journal 5a and from opposite sides , each of the correspondingly shaped areas of the sealing points 2a engage fully, tightly sealing (FIG. 2b).

The open position of the double-seat flap valve is shown in FIG. 2c. The opening movement of the counter shaft 3 is identified by O and its closing movement is identified by S. In this position, the two flaps 2 and the support 5 form a unit which accommodates and delimits the leakage space 16.

FIGS. 4 and 4a show the proposed double-seat flap valve in a third embodiment. In this case, a seat 9a for the flap 2 is formed on a sleeve-shaped axial slide 9, two of these axial slide 9 being arranged in the central housing part 1a and each being movable under prestress by means of a spring 10 to the axis of the pipeline and relative to the central housing part 1a are sealed. The springs 10 press the axial slide 9 against one another at their mutually facing end faces by means of two leakage space-set seals 11. In the area of the sealing of the two axial slides 9 with one another, the middle housing part 1a is penetrated by leakage openings 1e distributed over its circumference. The axial slide 9 are each sealed via an axial slide seal 15 with respect to the central housing part 1a. As long as the flaps 2 are in connection with the support 5 in the described unit in the open position (broken illustration of the flap 2 ^* and the support 5 *) or in the transverse position (see FIG. 4a), the two Axial slide 9 is compressed tightly via the two springs 10 arranged on the outside, so that the interior of the double-seat flap valve is tightly sealed from its surroundings. When the flaps 2 come into contact with the assigned seating surfaces 9a in the course of their displacement movement in the direction of the axis of the pipeline, they press them in the further course Sliding movement of the axial slide 9 apart (see FIG. 4) and thereby the leakage holes 1e distributed over the circumference of the central housing part 1a are released. During the closing movement, the movement process described takes place in reverse order. It is not difficult to design the leakage openings 1e in such a way that they have a total of at least one passage cross section corresponding to the nominal cross section of the largest pipe connected to the valve. The above embodiment is fully functional if the support ring 5 is dispensed with entirely and the unit delimiting the leakage space 16 consists solely of the flaps 2.

FIG. 5 shows how the proposed double-seat flap valve can be used to produce a pipe connection from pipes which intersect at a distance. The housing 1 of the valve is in its shortest possible dimension a on the one hand at a first connection opening 12a of the tube 12 formed by a first connection piece 12b (recess) and on the other hand at a second connection opening 13a formed by a second connection socket 13b (also recessed part) of the tube 13 connected. It can be seen that it is possible with the new double-seat flap valve to create an almost dead space-free and extremely short connection between the beican pipes 12 and 13.

If, as shown in FIG. 2d, the middle housing part 1a is made entirely of a suitable sealing material, then in relation to the design of the flaps 2 and with regard to the implementation of the shaft journals 5a through the middle housing part 1a (omission of the seals and the precautions necessary for their inclusion) a very simple and therefore inexpensive solution. With this embodiment it can be achieved that the valve switches absolutely leak-free.

A sheathing of the axial slide 9 with a suitable sealing material (FIGS. 4b and 4c) likewise simplifies the double-seat flap valve in the proposed fourth embodiment. Discrete flap seals 2a, axial slide seals 15 and leakage space seals 11 are no longer necessary. This is also absolutely leak-free switching possible.

The application variant according to FIG. 5 and the embodiments according to FIGS. 2d, 4b and 4c can also be carried out without the support ring 5; The functionality of the double seat flap valve in this regard remains unrestricted. FIG. 6 shows an embodiment of the proposed double-seat flap valve which is used when, based on the position of the valve, a shut-off valve, not shown there, is arranged in the pipeline to the right of the flap 2. If this shut-off valve is closed and there is an incompressible medium in the pipeline, the flap 2 assigned to the closed pipeline is first shifted into its end position on the seat surface 1d (closing days). In the course of this displacement, the displaced, incompressible medium can flow out through the second opening 18b of the compensating bore 18 and, via its first opening 18a, reaches an inner region of the middle housing part 1a behind the second flap 2, which has not yet been displaced from its central position End position (closed position) are transferred. For this purpose, a drive 7 is to be provided which decouples the opposite, translational displacement of the two flaps 2 from one another.

The invention has been described in the context of three preferred embodiments, but it goes without saying that, in practice, experts can implement further variants without leaving the scope of the invention and the industrial property rights to which it is entitled. This applies particularly to the closing devices of the leakage openings. Known closure organs such as valves, ball valves or butterfly valves can also be used here. With regard to the opposite movement of the flaps in their closed position during the closing or opening process of the valve, such known kinematic solutions can be used in which an adjusting movement (rotational or translational movement) of the valve drive into the desired form of movement of the valve

(translatory displacement movement, rotary movement) is implemented and in addition, an exact parallel guidance of the two flaps is ensured (for example, toggle lever drive or hydraulic drive between the Kiappen).

Claims

claims

1 double-seat flap valve with leakage protection, in particular as a shut-off device in pipes for the safe separation of hostile fluids, especially for food and beverage industries, with two disk-shaped flaps, which in their respective closed positions in mutually essentially parallel planes transverse to the axis of the Rohrieitung are oriented and thereby each by means of

Seal the sealing point in its circumferential area with respect to a seat-side surface of the valve, which is brought into its open position by a respective rotary movement in each case in a plane transverse to its position in the firing division and which in the closed position has a leakage space between it. limit the at least one controlled connection path to the environment of the

Valve, characterized in that

• that the flaps (2) during the opening process from their closed position while maintaining a sealing effect of their sealing points (2a) arranged on the circumference with respect to the housing inner wall of an assigned central housing part (1 a; 9) initially coaxially to the axis of the pipeline and are moved in opposite directions to each other,

Until they form a unit (2.2; 2.5.2) accommodating the leakage space (16),

• The total of two coaxial shaft journals (5a) arranged on opposite sides of the unit (2,2; 2,5,2) is directly or indirectly rotatably mounted in the housing part (1a) and is brought into the open position via this bearing.

2. Double-seat flap valve with leakage protection according to claim 1, characterized in that the two flaps (2) each come into contact with one another on their circumference and thereby sealingly via the sealing parts (2a) and in this position the leakage space (16) accommodating and form a limiting unit (2,2).

3. Double-seat flap valve with leakage protection according to claim 1, characterized in that the flaps (2) in each case via the sealing point (2a) on their circumference on a support (5) arranged between the flaps (2), on both sides come into contact with this and in each case circumferentially sealing, the two flaps (2) and the support (5) in this position forming the unit (2,5,2) which receives and delimits the leakage space (16).

Double-seat flap valve with leakage protection according to claim 1 or 2, characterized in that in the course of the opening or closing process and in the open position of the valve the leakage space (16) between the flaps (2) is limited in that the flaps (2) predominantly seal one another via these sealing points (2a), and that the shaft journals (5a), in the area of the sealing points (2a) crossing or tangent to them, there in their entirety by means of sealing elements (2a) correspondingly adapted to the shaft journals (5a), πng to be sealed.

5. Double-seat flap valve with leakage protection according to claim 1 or 3, characterized in that in the course of the opening or closing process and in the open position of the valve, the leakage space (16) between the flaps (2) is limited in that the on the support ring ( 5) arranged shaft journals (5a), in the area of the sealing points (2a) crossing or tangent to them, where they are enclosed in a volume-sealing manner by sealing points (2a) correspondingly adapted in their shape to the shaft journals (5a).

6. Double-seat flap valve with leakage protection according to claim 5, characterized in that the support ring (5) each in the region of its transition to the respective shaft journal (5a) with a concentric to the latter, engaging in the support ring (5) engaging annular recess (5k) In the course of the opening or closing process and in the open position, perpendicularly to the axis of the shaft journals (5a) and from opposite sides, correspondingly shaped areas of the sealing element (2a) engage in an annular sealing manner.

7. Double-seat flap valve with leakage protection according to one of claims 1 to 6, characterized in that the two shaft journals (5a) are each accommodated in a shaft bearing (6c or 6d) in the housing (1; 1a), the shaft bearing (6c, 6d) are each provided with longitudinal grooves (6e) which pass through the entire shaft bearing (6c, 6d) in a fluid-permeable manner.

8. Double-seat flap valve with leakage protection according to one of claims 1 to 7, characterized in that the flaps (2) in their closed position are steueΦar pressed against the seat surfaces (1d and 9a) in the direction of the axis of the pipeline.

9. Double-seat flap valve with leakage protection according to one of claims 1 to 8, characterized in that the leakage space (16) in the open position of the valve has at least one controlled VeΦindungsweg (5c, 5d) to the surroundings of the valve.

10. Double-seat flap valve with leakage protection according to one of claims 1 to 9, characterized in that the displacement of the flaps (2) in the direction of the axis of the pipeline takes place in such a way that the flaps (2) guide each other or that they each in or on or on the support ring (5) or in a gear box (5 *).

11. Double-seat flap valve with leakage protection according to one of claims 1 to 10, characterized in that the two sealing points (2a) are each realized by valve-side sealing means.

12. Double-seat flap valve with leakage protection according to one of claims 1 to 10, characterized in that the two sealing points (2a) are each realized by housing-side sealing means.

13. Double-seat flap valve with leakage protection according to claim 11 or 12, characterized in that the sealing means (2a) are designed as discrete seals.

14. Double-seat flap valve with leakage protection according to claim 11 or 12, characterized in that the sealing means (2a) by coating or

The flaps (2) or the middle housing part (1a; 9) can be encased with a suitable sealing material.

15. Double-seat flap valve with leakage protection according to claim 11 or 12, characterized in that the flaps (2) or the middle housing part

(1a; 9) are made of a suitable sealing material.

16. Double-seat flap valve with leakage protection according to one of claims 1 to 15, characterized in that the switching movement of the valve for generating the opposing displacement movement of the flaps (2) and the rotary movement of the unit (2.2; 2.5 , 2) is caused by a single drive (7).

17. Double-seat flap valve with leakage protection according to claim 16, characterized in that the drive (7) drives a translationally displaceable drive rod (3) within the shaft journal (5a) which acts as a bilateral between the two shaft journal (5a) Rack (3b) is designed so that each toothing of the rack (3b) is in engagement with a gear (3c, 3d) arranged between the two flaps (2), that the gear (3c, 3d) is coaxially drilled through and in this respective bore one behind the other, in the center of the gearwheel (3c, 3d) spaced from one another by a circumferential groove-shaped recess (3g), has two female threads with opposite pitch that parallel to the displacement movement of the flaps (2) have two threads on each of them debolzen (3e, 3f; 3e \ 3f) are attached, each of which engages in an associated nut thread of the gears (3c, 3d), that the gears (3c, 3d) and the rack (3b) in one the ripple Apfen (5a) carrying gear box (5 *) are arranged, and that the gear box (5 *) in the respective penetration area of its four threaded bolts (3e, 3f, 3e ', 3f) with respect to the interior of the housing (1; 1a ) is each sealed by a bellows (17) enveloping the respective threaded bolt (3e, 3f, 3e ', 3f) and connecting the gearbox (5 *) to the area of the flaps (2) in question.

18. Double-seat flap valve with leakage protection according to claim 16, characterized in that the drive (7) provides a pressure medium (D2) with which the displacement movement of the flaps (2) in the direction of the axis of the pipeline by one between the flaps ( 2) arranged pressure medium-operated second drive is effected.

19. Double-seat flap valve with leakage protection according to claim 16, characterized in that the drive (7) via a drive shaft (3) provides a rotary movement with which a knee-like arrangement (3a, G2, 4, G1, 2b) actuates is used to generate the displacement movement of the flaps (2) in the direction of the axis of the pipeline.

20. Double-seat flap valve with leakage protection according to one of claims 1 to 19, characterized in that the seat surface (9a) is formed on a sleeve-shaped axial slide (9), and that two of these axial slide (9) in the central housing part (1a) arranged and each preloaded by means of a spring (10) coaxial to the axis of the pipeline and each sealingly mounted with respect to the central housing part (1a), the two springs (10) of the axial slides (9) on their facing end faces by means of two leakage chamber sides Press seals (11) against each other and press the flaps (2) apart on their axial displacement into their closing division, the two axial slides (9) over the assigned seating surfaces (9a) and thereby the leakage openings distributed over the circumference of the central housing part (1a) Release gene (1e).

21. Double-seat flap valve with leakage protection according to claim 20, characterized in that the leakage openings (1e) have at least one passage cross-section corresponding to the nominal cross section of the largest pipe connected to the valve.

22. Double-seat flap valve with leakage protection according to one of claims 1 to 21, characterized in that in the housing inner wall of the middle

At least one compensating bore (18) is provided in the housing part (1a), which in each case on the one hand via a first opening (18a) and on the other hand a second opening (18b) in the vicinity of the respective seat surface (1d) into the interior of the center ren housing part (1a) opens out.