阅读说明：本技术 膜片密封的双座阀以及驱动器 (Diaphragm-sealed double seat valve and actuator ) 是由 J·布尔梅斯特 J·皮普洛 S·泰格特迈尔 于 2018-05-14 设计创作，主要内容包括：本发明涉及一种双座阀,具有：被分配给第一阀座(34)的第一关闭元件(14)；以及被分配给第二阀座(40)的第二关闭元件(16)；与第二关闭元件相连接的空心杆(20)；与第一关闭元件相连接的且以穿过空心杆的方式布置的阀杆(18)；固定在空心杆和双座阀的壳体(2)上的第一膜片(44)；以及以密封在阀杆和空心杆之间的通道(58)的方式布置的第二膜片(56),其中,第二关闭元件包括环形体(72),环形体在连接区域(120)中与承载区段(68)相连接,其中,环形体和承载区段设置成用于夹紧第二膜片,并且通过第二膜片和间隙密封件(78)使连接区域相对于内部空间(54)密封。为了简化结构并且为了保证在卫生条件下的可靠的功能,承载区段(68)具有泄漏通道(122),泄漏通道形成在连接区域和通道之间的流体连接的一个区段。(The invention relates to a double seat valve, comprising: a first closing element (14) assigned to the first valve seat (34); and a second closing element (16) assigned to the second valve seat (40); a hollow rod (20) connected to the second closing element; a valve rod (18) connected to the first closing element and arranged in such a way as to pass through the hollow rod; a first diaphragm (44) fixed to the hollow stem and to the housing (2) of the double seat valve; and a second diaphragm (56) arranged in such a way as to seal the passage (58) between the valve stem and the hollow stem, wherein the second closing element comprises an annular body (72) which is connected to the carrier section (68) in a connecting region (120), wherein the annular body and the carrier section are provided for clamping the second diaphragm and sealing the connecting region from the interior (54) by means of the second diaphragm and a gap seal (78). In order to simplify the construction and to ensure reliable functioning in hygienic conditions, the carrier section (68) has a leakage channel (122) which forms a section of the fluid connection between the connection region and the channel.)

1. A double seat valve having: a first closing element (14) assigned to the first valve seat (34); a second closing element (16; 16') assigned to the second valve seat (40); a hollow rod (20) connected to the second closing element (16; 16'); a valve rod (18) connected to the first closing element (14) and arranged through the hollow rod (20); a first membrane (44) fixed to the hollow rod (20) and to the housing (2) of the double seat valve; and a second diaphragm (56) arranged in such a way as to seal a channel (58) between the valve rod (18) and the hollow rod (20), wherein the second closing element (16; 16') comprises an annular body (72; 72') which is connected to the carrying section (68) in a connecting region (120), wherein the annular body (72; 72') and the carrying section (68) are provided for clamping the second diaphragm (56), and the connecting region (120) is sealed off from the interior (54) by the second diaphragm (56) and a gap seal (78), characterized in that the carrying section (68) has a leakage channel (122) which forms one section of the fluid connection between the connecting region (120) and the channel (58).

2. Double seat valve according to claim 1, characterised in that the hollow stem (20) passes through the first membrane (44) and the first clamping element (50) in one piece in the direction of the lifting axis (H).

3. Double seat valve according to claim 1 or 2, characterised in that a second bearing (70) is arranged in such a way as to support and guide the second clamping element (64).

4. A double seat valve according to any one of the preceding claims, wherein the clearance seal (78) is arranged and arranged to co-act with the second valve seat (40).

5. Double seat valve according to claim 4, characterised in that fixing means (88) preventing the annular body (72) and the carrying section (68) from rotating relative to each other are arranged on the second closing element (16; 16').

6. A double seat valve according to any one of the preceding claims, wherein the main drive (24; 24') has a piston (98) movable in a cylinder (92, 94), a drive rod (106) and a spring (102), and is provided with a first rotational stabilization mechanism which stabilizes the lifting movement of at least one of the valve stem (18) and the hollow stem (20) against rotation.

7. A double seat valve according to claim 6, wherein the first rotational stabilization mechanism comprises a sliding bearing that rotatably supports the piston (98) on the drive rod (106).

8. A double seat valve according to claim 6, wherein the first rotational stabilization mechanism comprises a piston section (130) having a recess (132) receiving one rod (134), wherein the rod is movable in the recess (132) only in the direction of the lifting axis (H).

9. A double seat valve according to any one of claims 6-8, wherein an auxiliary drive (26) is provided, which comprises a second rotational stabilizing mechanism.

Technical Field

The present invention relates to a diaphragm-sealed double seat valve according to the preamble of claim 1.

Background

In the prior art, single-seat valves are known, for example from WO 2013/170931 a1, which have a substantially annular diaphragm with an inner edge and an outer edge, and the inner edge of the diaphragm is fixed indirectly or directly to the closing element and the outer edge of the diaphragm is fixed to the housing of the single-seat valve.

Double seat valves are the same field of application, in which there are first and second closing elements which interact with associated valve seats, respectively, wherein the closing elements can be brought into a venting position independently of one another. In such a valve, the aim is to arrange the second diaphragm between the closing elements. Thus, the gap between the valve stems telescopically engaging into each other should be sealed.

Various solutions have been proposed in the prior art, in particular patent documents DE 102006025653a1 and EP 2734757B 1. Two valves proposed here have a valve stem and a closing body which consists of a plurality of individual parts.

Disclosure of Invention

The object of the present invention is now to propose a double seat valve with two diaphragms which has a simple structure and ensures its reliable function.

This object is achieved by a double seat valve having the features of claim one. Advantageous refinements are specified in the dependent claims.

A double seat valve is proposed, having: first and second closure elements assigned to the first and second valve seats; a hollow rod connected to the second closing element; and a valve stem connected to the first closing element and arranged in such a way as to pass through the hollow stem; a first diaphragm secured to the hollow stem and to the housing of the double seat valve; and a second diaphragm arranged in such a way as to seal the passage between the valve stem and the hollow stem, wherein the second closing element comprises an annular body connected to a carrier section, wherein the annular body and the carrier section are provided for clamping the second diaphragm and are sealed from one another by the second diaphragm and a gap seal. The carrier section has a leakage channel which forms one section of the fluid connection between the connection region and the channel. This can be demonstrated according to the proposed construction if the second diaphragm or the gap seal is not sealed and fluid enters the connection region. In the case of the use of two diaphragms, this means a hygienic construction which has evidence of a reliable functional limitation in operation, for example a failure of the second diaphragm. Compared to the prior art, the construction has fewer individual parts and is therefore more cost-effective on the one hand and faster and more reliable in assembly and maintenance on the other hand.

In addition, the structure of the double seat valve is simplified if the hollow rod passes through the first diaphragm and the first clamping element in one piece in the direction of the lifting axis. This also eliminates possible damage points.

A further advantageous development provides that the second support is arranged in such a way as to support and guide the second clamping element. A wide gap between the valve rod and the hollow rod is thereby completely achieved. This gap in turn means a more reliable and better indication of leakage that occurs when the second diaphragm or gap seal fails.

In a further development of the double seat valve, it is provided that the gap seal is provided and arranged to interact with the second valve seat. Thereby, the valve can be cleaned better and the locations where deposition of fluid residues may occur are reduced.

In a development of the double seat valve, a securing means is arranged on the second closing element, which securing means prevents a rotation of the first and second part relative to each other. This ensures a reliable function of the double seat valve and prevents the connection of the first and second parts from being released, in particular during operation.

The sealing function and the service life of the membrane are improved when the introduction of torsional forces which lead to mechanical loads on the membrane itself and on the clamping points of the membrane is prevented. In order to achieve this, it is proposed that the main drive has a piston which is movable in a cylinder, a drive rod and a spring, and that a first rotation stabilization mechanism is provided which stabilizes the lifting movement of the valve rod and the hollow rod against rotation.

In a first embodiment of the rotational stabilization mechanism, it is provided that the rotational stabilization mechanism comprises a sliding bearing which rotatably supports the piston on the drive rod. This is a cost-effective and reliable implementation.

A further cost-effective embodiment of the rotational stabilization device provides that the first rotational stabilization device comprises a piston section having a recess which receives a rod, wherein the rod can move in the recess only in the direction of the lifting axis.

If an auxiliary drive is provided, a second rotational stabilization mechanism may be provided in the auxiliary drive. This makes it possible to prevent torsional forces from acting on the valve rod and/or the hollow rod on the drive side. This simplifies the valve structure in the region of the valve stem and the hollow stem.

The illustrated design is advantageous because it enables large particles in the fluid to flow through the double seat valve and avoids clogging.

Drawings

The invention is explained below on the basis of examples and its advantages are explained.

Wherein:

FIG. 1 shows a cross section through a double seat valve with two diaphragms;

FIG. 2 shows a cut-away detail view of a region of the second diaphragm;

FIG. 3 illustrates a cut-away detail view of the double seat valve showing a separate seal groove in the second disc;

fig. 4 shows a section through a pneumatic drive.

Detailed Description

The double seat valve is shown in fig. 1 in a section along the lifting longitudinal axis H. The double seat valve has a housing 2 with a first connection 4 and a second connection 6. A fluid path is formed in the housing 2 between the first and second connections 4 and 6, which extends partially in the intermediate chamber 8.

The first side valve 10 and preferably the second side valve 12 are coupled to the housing 2 in such a way that they can be fluidically connected to the intermediate chamber 8. With the side valves 10 and 12, for example, leakage can be conducted from the intermediate chamber 8 out of the double seat valve and the intermediate chamber 8 can be cleaned. It is also possible to construct a sterile barrier, for example a moisture barrier, in the intermediate chamber 8. Advantageously, at least one of the side valves 10 and 12 is coupled to the intermediate chamber 8 in such a way that the fluid flows out of the intermediate chamber without any residue when the lifting axis H is oriented parallel to the force of gravity.

Within the housing 2, the first and second closing elements 14 and 16 are arranged such that they are movable along the lifting axis H. The first closing element 14 is connected to a valve stem 18. The second closing element 16 is connected to a hollow rod 20, wherein the valve rod 18 is arranged within the hollow rod 20 at least over a part of its extension, and the valve rod 18 and the hollow rod 20 extend along the lifting axis H and are embodied in one piece or in multiple pieces. The rods 18 and 20 are guided out of the housing 2 and through the housing part 22. Outside the housing 2, the valve rod 18 and the hollow rod 20 are operatively connected to a main drive 24.

The main drive 24 is preferably embodied as a pneumatic drive and is provided to bring about the open position and the closed position of the double seat valve. In the open position, a fluid connection between the first connection and the second connection is established, which is interrupted in the closed position. The assembly consisting of the valve rod 18, the hollow rod 20 and the main drive 24 can be embodied such that the valve rod 18 is moved by the action of the main drive 24 and the hollow rod 20 is moved as a result of this movement.

An auxiliary drive 26, which is likewise embodied as a pneumatic drive, can be provided. The auxiliary drive 26 is preferably arranged to move the valve rod 18 and the hollow rod 20 along the lifting axis H independently of one another. At this point, the levers 18 and 20 are brought into a partially raised position in which one of the closure elements 14 and 16, respectively, remains in the closed position, while the other closure element 14 and 16, respectively, is brought into the open position.

The drivers 24 and 26 are mechanically connected to the housing member 22, either directly or indirectly. The housing part 22 has a leakage outlet 28, through which a collection chamber 30 within the housing part can be connected to the environment U of the housing part.

For better illustration, this region of the housing 2 is shown in a detail view in section in fig. 2.

On the first closing element 14, a first seal 32 is received in the groove. In the closed position of the first closing element 14, the first seal 32 interacts sealingly with the first valve seat 34. The first seal 32 is embodied as an axial seal or as a semi-axial seal. The first closing element 14 can have a first projection 36, which is arranged and designed such that, in the partially lifted position of the first closing element 14, a throttle gap is formed between the first projection 36 and the housing 2. The throttle gap in particular causes an acceleration of the fluid flowing through the throttle gap and thus improves the cleaning in the partial lift position.

On the second closing element 16, a second seal 38 is received in the groove. In the closed position of the second closing element 16, the second seal 38 interacts sealingly with the second valve seat 40. The second seal 38 is embodied as an axial seal or as a semi-axial seal. The second closing element 16 can have a second projection 42, which is arranged and designed in such a way that, in the partially lifted position of the second closing element 16, a throttle gap is formed between the second projection 42 and the housing 2.

The first diaphragm 44, which is of substantially annular design, has an outer edge 46, which is fixed between the housing part 22 and the housing 2. To achieve the lift, the first diaphragm 44 has a wave-shaped cross section, so that the inner edge 48 of the first diaphragm 44 is turned inside out in a dome-like manner. The inner rim 48 is secured to the hollow bar 20. For this purpose, a first clamping element 50 can be provided, which can be fixed on the hollow rod 20. Advantageously, the clamping element 50 is designed such that the first diaphragm 44 bears locally against the furniture element 50, so that the first diaphragm 44 is relieved of the fluid pressure in the double seat valve. On the outer wall of the clamping element 50, a leakage groove 124 may be provided, which preferably extends substantially in the direction of the lifting axis H. The leakage groove can be embodied to extend only over the part of the outer wall facing away from the diaphragm 44 and to cooperate in a fluid-conducting manner with the transverse channel 126 in the housing part 22. Leaks that cause leaks in the first diaphragm 44 can be discharged from the double seat valve by means of the leakage groove 124 and the optional transverse channel 126, and the presence of leaks can thus be more reliably detected.

A recess is provided in the housing part 22, which receives the clamping element 50. In this recess a first bearing 52 is arranged, which slidingly bears the clamping element 50, so that the clamping element can move along the lifting axis H in the recess.

The first diaphragm 44 thus arranged seals the interior space 54 of the double seat valve from the environment U.

A second diaphragm 56 is arranged on the second closing element 16 so that a passage 58 formed between the valve stem 18 and the hollow stem 20 is sealed with respect to the intermediate chamber 8.

Second diaphragm 56 has an inner edge 60, inner edge 60 being clamped between a step 62 on valve stem 18 and a second clamping element 64 and thereby being fixed. The second clamping element 64 is received in a widened portion 66 of the channel 58, wherein the widened portion 66 is arranged in a carrier section 68 of the hollow rod 20. The second support 70 is received in the carrier section 68. The position and material of the second bearing 70 are selected such that the axial movement of the second clamping element 64 in the widened portion 66 is guided and supported. In this way, the second clamping element 64 is supported directly and the valve stem 18 is supported indirectly and is guided along the lifting axis H in the lifting movement. This guidance is very precise, since it is guided over a large diameter. Furthermore, this construction enables a passage 58 with a larger flow cross section than in the known prior art. The indication of a leak, for example indicating the need to replace the second diaphragm 56, is thus significantly improved.

The carrying section 68 carries an annular body 72, which forms part of the second closing element 16 and carries the second seal 38. The threads 74 establish a releasable connection between the carrier section 68 and the ring body 72. The outer edge 76 of the second membrane 60 is supported between the carrier section 68 and the annular body 72, in particular by suitable guidance and clamping and form-locking. The second membrane 60 simultaneously causes the sealing of the thread 74 with respect to the intermediate chamber 8. The connection of the carrying section 68 and the annular body 72 facing the interior space 54 and thus the thread 74 is sealed by a gap seal 78. The gap seal 78 is advantageously received in a groove on the carrier section 68 and is first fitted in this groove before the annular body 72 is screwed onto the thread 74. This embodiment makes it possible for the surfaces of the carrier portion 68 and of the annular body 72 facing the interior 54 to be beveled and shaped to flow away particularly well, so that fluid flows away from the second closing element 16 without leaving residues, without being impeded by the gap seal 18.

A hollow pin 80 is supported in the hollow rod 20 and passes through an elongated hole 82 in the valve stem 18. The slot 82 is arranged and shaped in such a way that it, in cooperation with the hollow pin 80, permits a relative movement of the valve rod 18 relative to the hollow rod 20 along the lifting axis H, but prevents a rotational movement of the rods 18 and 20 relative to each other. This prevents torsional loading of the second diaphragm 56. The hollow pin 80 may also be embodied as a cylindrical pin made of a solid material.

Fig. 3 shows a modification of the double seat valve, which relates in particular to the gap seal 78 and the second seal 38.

The first closing element 14, as well as the valve stem 18 and the hollow stem 20, are used unchanged from the example described above. The main modification relates to the second closing element 16'.

The second closing element 16' comprises an annular body 72', which annular body 72' is connected to the carrier section 68', for example by means of a thread 74 '. To simplify the sealing arrangement and to eliminate the seals, in the connecting region 120, a joint 84 is formed between the carrier section 68 'and the annular body 72' in such a way that it ends at a sealing groove 86 formed to receive the gap seal 78. The contour of the seal groove 86 may extend partially in the carrier section 68 'and the annular body 72'. By means of this embodiment, the gap seal 78, in addition to the sealing connection region 120, additionally assumes the function of the second seal 38 and interacts with the second valve seat 40. In addition to the reduced number of components, an additional advantage is obtained in particular in that a more hygienic construction is obtained, since the assembly can be cleaned more easily.

In order to prevent the threaded connection between the carrier section 68 'and the annular body 72' from loosening, it is advantageous to provide a fixing means 88, for example a countersunk screw. The securing means 88 forms a rotationally secure positive connection with the annular body 72 'and the carrier section 68'. Advantageously, the securing means is arranged on the base body of the sealing groove 86, so that in the assembled state of the double seat valve, the securing means is covered by the second seal 38 and thus the fluid in the double seat valve is inaccessible.

On the side facing away from the carrier section 68', the annular body 72' advantageously has at least one attachment face 90. The attachment surface is provided to co-act with a tool by means of which a threaded connection between the carrier section 68 'and the annular body 72' is established.

In fig. 4, a detail of an advantageous embodiment of the main drive 24 operating with pressure medium is shown.

The main drive 24 has a first cylindrical member 92 and a second cylindrical member 94. The posts 92 and 94 collectively form a drive housing and a working surface of the main drive 24. The piston seal 96, which is received in a peripheral groove of the piston 98, slides on the running surface. The piston 98 divides the interior space of the main drive 24 into two chambers. One chamber is a pressure medium chamber 100 into which a pressure medium, typically a gas, can be fed to generate a force acting on the piston 98, which force causes the piston 98 to move along the lifting axis H. Here, the force acts in a manner to overcome the return force generated by the spring 102 located in the spring chamber 104, which is the second chamber.

The piston 98 is fixed to a drive rod 106 and the lifting motion is transmitted to the drive rod 106. The drive rod 106 may be directly or indirectly connected to the valve stem 18 to cause movement of the first valve disc 14.

The drive rod 106 may have a pressure medium channel 108. At least one inlet 110 in the drive rod 106 establishes a fluid connection between the pressure medium channel 108 and the pressure medium chamber 100.

When the spring 102 is compressed and then expanded, a torque is generated by the torsion acting on the piston 98. In order to prevent this torque from being transmitted to the drive rod 106 and thus ultimately to the second diaphragm 56, a first rotational stabilization mechanism is provided. A cost-effective embodiment of the rotational stabilization means is a sliding bearing, with which the piston 98 is rotatably mounted on the drive rod 106. The first rotational stabilization mechanism or sliding bearing includes a bearing sleeve 112 having a flange 114. The bearing set together with the bearing race 116 form a sliding bearing for the piston 98. The fixing nut 118 fixes the sliding bearing and the piston 98 on the drive rod 106 and ensures a defined force ratio in the sliding bearing. The bearing sleeve 112 and bearing race 116 may be constructed of a cost-effective and suitable material, such as Polytetrafluoroethylene (PTFE).

An alternative embodiment of the first rotational stabilization mechanism in the main drive 24' is shown in fig. 5. The piston 98 comprises a piston section 130 which extends along the lifting axis H in such a way as to surround the drive rod 106 and is surrounded by the spring 102. The piston section 130 has a recess 132 that receives a rod 134 that is connected to the end plate of the first cylindrical member 92. The recess 130 extends in the direction of the lifting axis H and covers only a part of the circumference in the circumferential direction. The recesses 130 and the bars 134 are dimensioned such that the bars 134 can move in the direction of the lifting axis H, however, the movement in the circumferential direction is blocked. This can be achieved, for example, by a round rod which extends with its longitudinal axis in a longitudinal groove, the width of which corresponds approximately to the diameter of the round rod. In this way, it is prevented that the torsional force introduced into the piston 98 by the spring 102 causes the piston 98 to rotate and subsequently transmit this rotation to the drive rod 106.

Alternatively or in addition to the hollow pin 80 preventing the valve rod 18 and the hollow rod 20 from rotating relative to each other, a second rotational stabilization mechanism may also be provided in the auxiliary drive 26 in addition to the first rotational stabilization mechanism in the main drive 24, 24'. The second rotational stabilization mechanism can also be constructed, for example, according to the principle explained in fig. 4 and 5. The second rotational stabilization mechanism can also be embodied as a mechanical stop for the piston of the auxiliary drive 26 in the direction of rotation. By means of the rotational stabilization mechanism, the detrimental twisting effects on the diaphragms 44 and 56 are prevented and the service life of the diaphragms is increased.

List of reference numerals

2 casing

4 first interface

6 second interface

8 middle chamber

10 first side valve

12 second side valve

14 first closing element

16. 16' second closing element

18 valve stem

20 hollow bar

22 housing part

24. 24' main driver

26 auxiliary drive

28 leakage outlet

30 collection chamber

32 first seal

34 first valve seat

36 first projection

38 second seal

40 second valve seat

42 second projection

44 first diaphragm

46 outer edge of first membrane

48 inner edge of first diaphragm

50 first clamping element

52 first support

54 inner space

56 second diaphragm

58 channel

60 inner edge of second diaphragm

62 step part

64 second clamping element

66 widening

68. 68' load bearing section

70 second support

72. 72' Ring body

74. 74' thread

76 outer edge of the second membrane

78 Clearance seal

80 hollow pin

82 long hole

84 seam

86 seal groove

88 fixing device

90 attachment surface

92 first cylindrical member

94 second column piece

96 piston seal

98 piston

100 pressure medium chamber

102 spring

104 spring chamber

106 drive rod

108 pressure medium chamber

110 inlet

112 supporting member set

114 flange

116 bearing race

118 fixed nut

120 connecting segment

122 leakage path

124 leakage groove

126 transverse channel

130 piston section

132 recess

134 pole

136 connector