MEMBRANVENTIL

Description

[0001] The invention relates to a diaphragm valve of the type specified in the preamble of claim 1.

[0002] Diaphragm valves are well known from the prior art and generally comprise an actuator housing, a diaphragm, and a valve housing with at least one inlet and outlet. A valve seat—often in the form of a web—is arranged in the flow channel of the valve housing, i.e., between the inlet and outlet. The diaphragm, located above the valve seat and between the actuator and valve housings, seals the diaphragm valve to the outside via its outer edge section and serves as a valve element interacting with the valve seat. For this purpose, an inner section of the diaphragm is connected to an actuator located in the actuator housing, by means of which the diaphragm can be pressed onto the valve seat to close the flow channel or pulled away from the valve seat to open the flow channel. Such a diaphragm valve is known, for example, from DE 20 2014 102 658 U1.

[0003] Since the diaphragm is subject to heavy stresses due to the changing load and the different media of the process fluid, the diaphragms of the diaphragm valves must be replaced regularly.

[0004] Replacing the diaphragm is often cumbersome, and access to the connecting elements is difficult because the space around the built-in diaphragm valve is frequently obstructed by piping and other field equipment. Another disadvantage is that the valve bodies have different geometries and interfaces for mounting the actuator housings that contain the drive mechanism.

[0005] The generic EP 3 333 465 A1 discloses a diaphragm valve, according to the preamble of claim 1, in which an intermediate flange is provided between the actuator housing receiving the drive and the valve housing.

[0006] The invention is based on the objective of further developing a diaphragm valve according to the type specified in the preamble of claim 1 in such a way that, in addition to simplified attachment of an actuator housing to existing systems, in particular without replacing or modifying the valve housing which is permanently installed in the pipeline system, a quick and easy replacement of the diaphragm is also made possible.

[0007] This problem is solved by the characterizing features of claim 1 in conjunction with its preamble features.

[0008] The dependent claims constitute advantageous further developments of the invention.

[0009] In a known manner, the diaphragm valve comprises a valve housing with at least one flow channel for fluid flow and a valve seat, an actuator housing connectable to the valve housing and containing an actuator, and a diaphragm that separates the valve and actuator housings in a fluid-tight manner. The diaphragm is clamped along its edge region in the axial direction a and is held fluid-tight between the valve and actuator housings. It is operatively connected to the actuator located in the actuator housing in such a way that the diaphragm can be pressed onto the valve seat to close the flow channel or, conversely, pulled away from the valve seat to open the flow channel.

[0010] Furthermore, the actuator housing is connected to the valve housing via an intermediate flange that can be detachably connected to the valve housing, wherein the actuator housing can in turn be detachably connected to the intermediate flange in such a way that when the actuator housing is attached to the intermediate flange, the actuator housing exerts a pressure force on the edge area of ​​the diaphragm.

[0011] This design proves advantageous because, for the conversion of existing systems, only the intermediate flange needs to be adapted to the valve housing or to the existing flange connection of the valve housing, and thus no machining or replacement of the valve housing is required.

[0012] Furthermore, it is now possible to implement a uniform membrane replacement system for any valve housing type, since the flange connection between the intermediate flange and the valve housing does not need to be loosened.

[0013] Furthermore, the intermediate flange allows for adaptation to the given prevailing installation space conditions, so that simplified access to connecting elements can be ensured by appropriately designing the intermediate flange to the installation space conditions.

[0014] Furthermore, replacing or changing the membrane is quick and easy, because in addition to the simplified accessibility to the connecting elements – made possible by a corresponding design of the intermediate flange – the pressure force required to clamp the membrane is also generated when attaching the actuator housing to the intermediate flange.

[0015] To ensure a sufficiently large pressure force for clamping the diaphragm, the fastening means acting between the actuator housing and the intermediate flange are designed in such a way that when connecting the actuator housing to the intermediate flange, the actuator housing performs a relative movement in axial direction a with respect to the intermediate flange and thus with respect to the valve housing.

[0016] According to an unclaimed embodiment, the fastening means are designed in the form of an external thread formed on the intermediate flange and a union nut that circumferentially encloses the intermediate flange and the actuator housing and has an internal thread corresponding to the external thread. To exert a compressive force on the actuator housing when tightening the union nut, the union nut and the intermediate flange are in contact with each other in their overlap area (viewed in the axial direction a) via correspondingly arranged contact surfaces that are opposite each other in the axial direction a. Since only one central fastening element, namely the union nut, needs to be actuated, simple and quick disassembly and assembly of the two housing parts, and thus rapid replacement of the diaphragm, is possible.

[0017] According to a further, unclaimed embodiment, the fastening means are in the form of an internal thread formed on the intermediate flange and a corresponding external thread formed on the actuator housing. This means that the actuator housing can be connected directly to the intermediate flange by means of screws, and thus without additional fastening elements.

[0018] A sleeve can be provided – arranged axially between the externally threaded part of the actuator housing and the edge of the diaphragm – through which the force is transmitted from the actuator housing to the edge of the diaphragm when the actuator housing is screwed to the intermediate flange. The sleeve prevents a relative rotational movement between the edge of the diaphragm and the actuator housing, which could potentially damage the diaphragm. Generally, the differing coefficients of friction – namely, the coefficient of friction in the contact surface between the sleeve and the diaphragm (=> sleeve made of metal; diaphragm made of elastically deformable plastic, elastomer, rubber) being greater than the coefficient of friction in the contact surface between the actuator housing and the sleeve (=> both made of metal, plastic, or a combination thereof) – are sufficient to prevent a relative rotational movement between the sleeve and the edge of the diaphragm.Alternatively and / or additionally, an anti-rotation device can be provided between the sleeve and the intermediate flange.

[0019] According to the invention, the fastening means are designed in the form of a cam ring that partially overlaps the intermediate flange and the actuator housing in the axial direction a and circumferentially encloses the intermediate flange and the actuator housing, with a groove provided on its inner circumferential surface, as well as in the form of two first drive elements arranged on the actuator housing and positively guided in the groove, and two second drive elements arranged on the intermediate flange and positively guided in the groove, aligned with the first drive elements when viewed in the axial direction a. In order to exert a compressive force on the diaphragm during a rotational movement of the cam ring relative to the actuator housing and intermediate flange, the groove is designed with groove walls that have a ramped profile in opposite directions in certain areas.The phrase "opposite ramp-shaped progression" is to be understood in particular as meaning that, viewed in axial direction a, the upper groove wall is formed in a ramp-like manner downwards in some areas, reaching a maximum and then ramping upwards again, while the lower groove wall, viewed in axial direction a, is formed in this area in the opposite direction, i.e. ramping upwards, reaching a maximum and then ramping downwards.

[0020] This has the effect that, due to the now possible quick-release connection solution between actuator housing and intermediate flange, a particularly easy and quick change or replacement of the membrane is possible.

[0021] According to the invention, it is also provided that the cam ring has openings or passages to the groove aligned in the axial direction a, which are dimensioned and arranged in such a way that the drive elements arranged in the axial direction a can each be guided through them, so that by a corresponding rotation of the cam ring, i.e. into a position in which the openings or passages and drive elements are aligned with each other, simple disassembly or assembly is made possible.

[0022] Preferably, a small recess is also provided in the area of ​​the maximum of one or both ramps, so that a locking of the drive element in the closed position is advantageously made possible.

[0023] In order to ensure the most uniform force application possible when the cam ring rotates, the two first drive elements arranged on the actuator housing – and thus also the two second drive elements arranged in axial direction a aligned with the first drive elements on the intermediate flange – are preferably arranged opposite each other in radial direction r.

[0024] Preferably, the drive elements are designed as rotatably mounted rollers, which are supported by means of rolling bearings on pins arranged on the actuator housing or intermediate flange and aligned in the radial direction r. This advantageously enables particularly smooth actuation of the cam ring.

[0025] Preferably, the cam ring has a drive mechanism for applying torque. This ensures that the torque required to tension the diaphragm can be easily transferred to the cam ring.

[0026] Preferably, the drive is designed in the form of an easy-to-grip lever connected to the cam ring.

[0027] For reasons of installation space, the lever is preferably detachably connected to the cam ring.

[0028] Further advantages and application possibilities of the present invention will become apparent from the following description in conjunction with the exemplary embodiments shown in the drawings.

[0029] The description, claims, and drawing use the terms and associated reference numerals listed below. In the drawing, this means: Fig. 1a a sectional view of an unclaimed embodiment of a diaphragm valve; Fig. 1b the diaphragm valve made of Fig. 1a in a side view; Fig. 2a another, unclaimed embodiment of a diaphragm valve in a sectional view; Fig. 2a side view of the diaphragm valve made of Fig. 2a ; Fig. 3a a sectional view of a diaphragm valve according to the invention, and Fig. 3b the diaphragm valve made of Fig. 3a in a side view.

[0030] In the following description and figures, identical parts and components are marked with the same reference numerals to avoid repetition, unless further differentiation is necessary or makes sense.

[0031] Fig. 1a bis Fig. 3b Figure 10 shows a diaphragm valve. The diaphragm valve 10 essentially comprises a valve housing 12, an actuator housing 14, and a diaphragm 16 that separates the valve and actuator housings 12, 14 in a fluid-tight manner, wherein the diaphragm 16 is clamped over its edge region 16-1 in the axial direction a and is held fluid-tight between the valve and actuator housings 12, 14.

[0032] The valve housing 12 has an inlet and outlet 12-1, 12-2, as well as a valve seat 20 arranged in the flow channel 18 of the valve housing 12. An actuator, which is operatively connected to the diaphragm 16, is integrated into the actuator housing 14, via which the diaphragm 16 is actuated – as in Fig. 1 shown - can be pressed onto the valve seat 20 to close the valve or vice versa - can be pulled away from the valve seat 20 to open the valve.

[0033] The drive in question is a pneumatic drive, meaning it is powered by the supply of compressed air, which is introduced into the actuator housing 14 via corresponding openings 14-1. The supplied compressed air flows around a spring carrier 22 of a spring assembly 24 and enters a pressure chamber 26, which is bounded at the top by a movable piston 28. The pressure acts against the piston 28 and, once the preload force of the spring assembly 24 is exceeded, moves it upwards in the axial direction a. The upward movement is transmitted to the diaphragm 16 via a drive rod 30 connected to the piston 28 and a valve rod 32, which is axially movably mounted in the actuator housing 14 and rigidly connected to the drive rod 30 and the diaphragm 16. The diaphragm valve 10 shown is therefore a so-called air-to-open type or normally closed type, since it is held closed in the unpressurized state by the spring assembly 24.

[0034] The diaphragm valve 10 is characterized by the fact that an intermediate flange 34 is detachably attached to the valve housing 12, via which the valve housing 12 and actuator housing 14 are detachably connected to each other. As can be seen in particular from Fig. 1b , 2b and 3b As can be seen, the intermediate flange 34 is detachably connected to the valve housing 12 via several screw connections 36.

[0035] According to the in Fig. 1a und Fig. 1b In the illustrated embodiment, the actuator housing 14 is detachably connected to the intermediate flange 34 via a union nut 38. For this purpose, the intermediate flange 34 is provided radially on its outer surface with an external thread corresponding to the internal thread of the union nut 38. The union nut 38 and the actuator housing 14 are operatively connected via corresponding contact surfaces formed on the actuator housing 14 and the union nut 38, which are arranged opposite each other in the axial direction a. When the union nut 38 is tightened, the actuator housing 14 is moved downwards in the axial direction a, thereby clamping the edge region 16-1 of the diaphragm 16 fluid-tight between the valve housing 12 and the actuator housing 14.

[0036] The in Fig. 2a und 2b The further embodiment shown essentially corresponds to the one described in Fig. 1a und Fig. 1b depicted embodiment.

[0037] The in Fig. 2a und 2b The illustrated embodiment is characterized in that the actuator housing 14 is now attached directly to the intermediate flange 34, i.e., without an additional fastening means. For this purpose, the intermediate flange 34 is provided with an internal thread at its end region facing the actuator housing 14 when viewed in the axial direction a, and the actuator housing 14 has, correspondingly, an external thread at its end region facing the valve housing 12 when viewed in the axial direction a – a thread that corresponds to the internal thread of the intermediate flange 34 – so that the actuator housing 14 and the intermediate flange 34 can be screwed directly together.

[0038] How Fig. 2a As further shown, a sleeve 40 is arranged – viewed in the axial direction a – between the part of the actuator housing 14 with the external thread and the edge region 16-1 of the diaphragm 16. This means that the diaphragm 16, or rather the edge region 16-1 of the diaphragm 16, is held clamped between the valve housing 12 and the sleeve 40. In other words, when the actuator housing 14 and the intermediate flange 34 are screwed together, the force flows from the actuator housing 14 via the sleeve 40 to the edge region 16-1 of the diaphragm 16. Due to the different coefficients of friction in the respective contact surfaces, namely a small coefficient of friction in the contact surface between the actuator housing 14 and the sleeve 40 (=> metal-on-metal contact) versus a large coefficient of friction in the contact surface between the sleeve 40 and the diaphragm 16 (=> metal-on-elastomer contact), rotational movement of the sleeve 40 is prevented.The sleeve 40 performs only a straight-line movement in relation to the intermediate flange 34.

[0039] The in Fig. 3a und 3b The embodiment of the diaphragm valve 10 according to the invention, as illustrated, essentially corresponds to the one described in Fig. 1a, 1b as in Fig. 2a, 2b depicted embodiments.

[0040] Characteristic of the in Fig. 3a und 3b The embodiment of the diaphragm valve 10 shown in the invention is the now provided quick-release type connection between actuator housing 14 and intermediate flange 34.

[0041] For this purpose, two first drive elements 42 are arranged opposite each other on the actuator housing 14 – viewed in the radial direction r – while second drive elements 44 are provided on the intermediate flange 34, aligned with the first drive elements 42 in the axial direction a. Fig. 3a As can be seen, the drive elements 42, 44 are each designed in the form of rotatably mounted rollers, which are mounted by means of rolling bearings on pins arranged on the actuator housing 14 or intermediate flange 34 and aligned in the radial direction r.

[0042] The driving elements 42, 44 are guided by a cam ring 46 which circumferentially surrounds the actuator housing 14 and the intermediate flange 34 and partially overlaps the actuator housing 14 and the intermediate flange 34 in the axial direction a, and which has a corresponding groove 48 on its inner circumferential surface, cf. in particular Fig. 3b , exhibits, in which the first and second drive elements 42, 44 are forcibly guided.

[0043] As especially from Fig. 3bAs can be seen, the groove 48 is designed such that the upper groove wall 48-1, viewed in the axial direction a, has a ramped downward slope in some areas, reaching a maximum and then ramping upward again, while the lower groove wall 48-2, viewed in the axial direction a, has the opposite slope, i.e., ramping upward to a maximum and then ramping downward. A lever 50, which can be detachably attached to the cam ring 46, allows for simplified rotation of the cam ring 46 and thus clamping of the edge region 16-1 of the diaphragm 16 between the valve housing 12 and the actuator housing 14.

[0044] On the cam ring 46, corresponding openings or passages 52 are formed and arranged such that the first and second drive elements 42, 44, which are aligned with each other in the axial direction a, each fit through them and thus, after rotation of the cam ring 46 into a corresponding removal position, i.e. a position in which the openings or passages 52 are aligned with the respective first and second drive elements 42, 44, the actuator housing 14 together with its drive elements 42 can be removed. Reference symbol list

[0045] 10 Diaphragm valve 12 Valve housing 12-1 Inlet port 12-2 Outlet port 14 Actuator housing 16 Diaphragm 16-1 Diaphragm edge 18 Flow channel 20 Valve seat 22 Spring carrier 24 Spring assembly 26 Pressure chamber 28 Piston 30 Drive rod 32 Valve stem 34 Intermediate flange 36 Screw connection 38 Union nut 40 Sleeve 42 First drive elements 44 Second drive elements 46 Cam ring 48 Groove 48-1 Upper groove wall 48-2 Lower groove wall 50 Lever 52 Openings or passages aaxial direction radial direction

Claims

1. Diaphragm valve (10) comprising a valve housing (12) with at least one flow path (18) for the flow of a fluid through it and a valve seat (20), an actuator housing (14) connected to the valve housing (12) and having a drive, as well as a diaphragm (16) separating the valve and the actuator housing (12, 14) in a fluid-tight manner, which diaphragm (16) is clamped along its edge area (16-1), as viewed in the axial direction (a), and held in a fluid-tight manner between the valve and actuator housings (12, 14), and which diaphragm (16) is operatively connected to the drive arranged in the actuator housing (14) in such a way that the diaphragm (16) can be brought into contact with the valve seat (20) in order to close the flow path (18), wherein the actuator housing (14) is connected to the valve housing (12) via an spacer flange (34) which can be detachably connected to the valve housing (12), and wherein the actuator housing (14) can be attached in a detachable manner by means of the spacer flange (34) and in such a manner that it exerts a compressive force on the edge area (16-1) of the diaphragm (16), which actuator housing (14) can be connected to the spacer flange (34) via fastening means (38, 42, 44, 46), which fastening means (38, 42, 44, 46) are designed in such a way that, during connection, the actuator housing (14) will perform a relative movement in the axial direction (a) with respect to the spacer flange (34), characterized in that the fastening means are in the form of a slotted ring (46) which surrounds the spacer flange (34) and the actuator housing (14) circumferentially and which has a groove (48) formed on its inner circumferential surface, as well as two first entrainment elements (42) arranged on the actuator housing (14) and guided in the groove (48), and two second entrainment elements (44) arranged on the spacer flange (34) and guided in the groove (48), which first and second entrainment elements (42, 44), as viewed in the axial direction (a), are aligned with one another, and which groove (48), as viewed in the axial direction (a), has groove walls (48-1, 48-2), some areas of which are ramp-shaped in opposite directions, and in that the slotted ring (46) has openings (52) aligned in the axial direction (a) to the groove (48), which openings (52) are dimensioned and arranged so as to allow the entrainment elements (42, 44), which are arranged in alignment with one another in the axial direction (a), to pass through them.

2. Diaphragm valve (10) according to claim 1, characterized in that the first entrainment elements (42) arranged on the actuator housing (14) and the second entrainment elements (44) arranged on the spacer flange (34) are each arranged radially opposite one another3. Diaphragm valve (10) according to any one of claims 1 or 2, characterized in that the entrainment elements (42, 44) are each designed in the form of a roller that is rotatably mounted on a pin aligned in the radial direction (r) by means of a roller bearing.

4. Diaphragm valve (10) according to any one of claims 1 to 3, characterized in that the slotted ring (46) has a drive (50) for applying a torque.

5. Diaphragm valve (10) according to claim 4, characterized in that the drive is provided in the form of a lever (50) that is connected to the slotted ring (46).

6. Diaphragm valve (10) according to claim 5, characterized in that the lever (50) is detachably connected to the slotted ring (46).