HK1151573B - A process valve acting as a lift valve - Google Patents

Description

Process valve functioning as a poppet valve

Technical Field

The invention relates to a process valve functioning as a poppet valve, the valve having: a valve housing comprising at least one valve housing portion; at least a first and a second connecting tube connected to said valve housing portion and establishing communication to the interior cavity of the valve housing portion; a connecting opening arranged in the valve housing between the connecting pipes, in or on which at least one seat surface is formed; at least one translationally movable latch which interacts with the associated seat surface and controls the connection opening; a control rod which is fastened to any of the locking parts and is guided out of the valve housing in a sealing manner via a valve housing opening of the valve housing opposite the connecting opening and is connected to a drive piston of a servo drive; an isolator housing connects the valve housing to the servo actuator, the isolator housing having a mechanism for connection to the valve housing at least at its end on the side of the valve housing.

Background

A poppet valve of the type mentioned at the outset has the essential feature that the valve has at least one part of its displaceable opening and closing movement, which is designed as a closing part of one seating disk (single seat valve) or as a closing part of two seating disks (double seat valve), positioned perpendicular to an associated seating surface. However, within the scope of the above embodiments, the poppet valve can also be designed as a sliding valve, in which the locking part designed as a sliding piston or a plurality of locking parts designed as sliding pistons slide along an associated cylindrical seat surface during the displaced opening and locking movement. In double seat valves, it is also known to use a combination of a seat disc and a sliding piston.

A closure seal which is arranged in the seat disk interacts axially or axially/radially with the associated seat surface (sealing in so-called press-fit engagement); at the same time, a closure seal arranged in the sliding piston interacts radially with the associated cylindrical seat surface (seal in the so-called sliding engagement). The opening and closing movement with the displacement of the closing lock is effected via a pressure medium-loaded, preferably gas-loaded, piston drive, wherein the return movement of the drive piston is usually performed by means of a spring, preferably a helical spring. The piston drive can work spring-closed or spring-open against the latch and the associated seat surface. In order to reduce the opening force of the shut-off valve, the actuating lever of the closing part can be designed in the region of its passage through the valve housing in the form of a so-called pressure compensation piston, so that the force acting in the lifting direction on the closing part is compensated partially to completely on the projected end face of the pressure compensation piston, starting from the fluid (e.g. product) present in the valve housing.

In order to reliably separate a fluid present in the valve housing from the pressure medium acting on the drive piston in the servo drive, a so-called spacer housing (lantern housing) is arranged between the valve housing and the servo drive. The opening movement of the process valve is performed either upwards or downwards with respect to the vertical normal position of the valve, so that an upwards or downwards opening valve is referred to. Since a construction height which is as small as possible is always desirable downwards, the servo drives are usually arranged above the valve housing.

A critical selection criterion for such process valves is the downward height of the valve, but also its upward height. The latter is mainly determined by the design of the isolator housing and the servo driver, where, in order to reduce the structural height thereof, it is known to: the spring of the servo drive of a double seat valve is integrated completely into the installation space of the isolator housing (prior art, for example, according to EP 0646741B 1). In another known process valve, the valve has only one latching means, while the isolator housing is completely free of the relevant parts that contribute to the saving in terms of construction height (DE 20006594U 1). A comparative case is known from DE3835944a 1.

In the case of the double seat valves mentioned above, the control rod of the closing mechanism, in particular if the closing mechanism is designed as a sliding piston, is usually always designed in the form of the pressure compensation piston described above. In order to ensure that the forces acting on the respective closing mechanism can be adequately compensated for by corresponding reaction forces acting on the associated pressure compensation pistons, these pressure compensation pistons are, in cross section, always enlarged to a cross section that approximates the effective design of the associated closing mechanism. The large through-opening cross section through the valve housing thus determined makes it difficult to seal the pressure compensation piston, but on the other hand the pressure compensation piston provides a height-saving accommodation for the spring of the valve drive in its inner space.

The connection between the valve housing and the servo drive via the isolating body housing also has an influence on the overall height of the process valve concerned, which is rather small here. In this connection, in order to achieve such a connection, it is relevant to the extent that the connection has an impact on the assembly and disassembly outlay and on the costs. For decades, three related connections, briefly summarized below, have been used primarily.

One involves a connection using flanges that are screwed to each other. The patent documents EP 0646741B1 and EP 0174384B1 each propose an associated connection between the valve housing and the separator housing on a double seat valve. The connection is time-consuming to install or remove and rotation between the valve housing and the actuator is only possible within the circumferential pitch of the connecting screw.

Furthermore, in most process valves, it is mentioned that so-called clamping flange connections are currently selected, as disclosed in DE 20006594U1 (process valves having only one closing mechanism) or in DE3835944a1 or EP 0834689a1 (each of which relates to a double seat valve). The valve housing parts connected to one another each have a so-called clamping flange which is conically tapered on the outer side, facing radially outward. The flanges are held together by a partial clamping ring which surrounds the flange sides in an almost 360-degree manner and which compensates for the bevel, wherein the two clamping ring halves are connected to one another and held together either via a joint and a threaded connection or via two threaded connections. Such a connection is easy to install and remove and positioning of the actuator in relation to the valve housing is possible in any position. The costs for such a connection are after all higher than the costs for a flange connection realized with screws.

Finally, it is known that the connection between the valve housing and the actuator housing is effected via a screw connection (for example the so-called tube screw specified in DIN 11851 or DIN 11864) (WO 2007/128360a 1). In this case, the slotted nut is usually carried by the insulator housing, while the external thread is formed on the valve housing. This connection is preferred for aseptic processes because the grooved nut has a smaller contact surface for dirt than a screw-made flange connection or a clamping flange connection. The cost of the last connection is highest compared to the first two connections; those disadvantages of the foregoing approaches are not present.

DE 9013788U1 describes a connection for auxiliary devices for thermal energy and water supply, in particular for water meters, thermal energy meters or filter cartridges, with a shut-off valve which is rotatably mounted in a housing between a through position and a shut-off position, and with a cartridge for the auxiliary device which is releasably connected to the housing. The sleeve head is connected to the housing by means of a bayonet connection, on which a pin is guided in an L-shaped groove. The sleeve and the shut-off valve are coupled (this means in particular a locking connection in the circumferential direction, but not an axial clamping connection) in such a way that the shut-off valve is opened when the sleeve is mounted on the housing; when the sleeve head is detached, the stop valve is closed. In order to positively effect a force-locking connection of the sleeve and the shut-off valve, it is advantageous if a connecting means (pin bore) is connected to the sleeve, which connecting means is connectable to a symmetrical connecting means (pin) of the valve. When the sleeve head is mounted, the connection means is connected in a force-fitting manner to the symmetrical connection means (the pin engages in the pin hole), and the movement of the sleeve head is transmitted (in the circumferential direction) to the valve, which opens or closes accordingly.

In WO 2007/128360a 1a valve housing assembly for a monitoring system, a control system and a regulating system of a process valve is described. The valve housing assembly concerned consists of an array of individual valve housing heads which are connected to one another via a bayonet-like connection.

Disclosure of Invention

The object of the invention is to provide a device of the type mentioned at the outset for connecting a valve housing to a servo drive in a process valve which functions as a poppet valve, which device has a lower overall height and a lower cost than all known devices of this type, and which device, moreover, has the greatest safety in opening and is of a simple construction.

To this end, the invention provides a process valve which functions as a poppet valve, having: a valve housing comprising at least one valve housing portion; at least a first and a second connecting tube connected to said valve housing portion and establishing communication to the interior cavity of the valve housing portion; a connecting opening arranged in the valve housing between the connecting pipes, in or on which at least one seat surface is formed; at least one translationally movable latch which interacts with the associated seat surface and controls the connection opening; a control rod which is fastened to any of the locking parts and is guided out of the valve housing in a sealing manner via a valve housing opening of the valve housing opposite the connecting opening and is connected to a drive piston of a servo drive; an isolator housing for connecting a valve housing to a servo actuator, the isolator housing having a mechanism for connection to the valve housing at least at an end thereof on one side of the valve housing, wherein: the isolator shell is fixed on the valve shell through a bayonet type connecting mechanism; the separator housing has at its end on the valve housing side at least two plug-in lugs projecting radially inward in the radial direction on the separator side, which are each delimited on both sides by a plug-in recess formed between them on the separator side; the valve housing has a corresponding number of valve housing-side latching lugs which project radially outward in the circumferential region of the valve housing opening on the outside and which are each delimited on both sides by a latching recess which is formed between them and is located on the valve housing side, wherein the latching lugs on the isolator side engage in the valve housing-side latching recesses in the open position of the bayonet coupling and the latching lugs on the valve housing side engage behind in the closed position of the bayonet coupling in an almost overlapping manner; and the bayonet connection is self-locking in a form-locking manner in the locking position thereof; the spacer housing has a slot in the circumferential extension of at least one plug-in lug on the side of the spacer, which slot extends axially into the spacer housing from the end of the spacer housing on the side of the valve housing and, viewed radially, extends through from the inside to the outside; each bayonet-type flange on the valve housing side has, radially on the outside, a groove-shaped recess which is limited in its radial depth and its circumferential extent, wherein, in the closed position of the bayonet connection, the recess is positioned, as viewed in the circumferential direction, in superimposition with the associated groove; the actuating lever is guided in a tubular support sleeve which is arranged inside the spacer housing and is fixed and which makes the most of the axial length of the spacer housing; in the end region of the support sleeve on the valve housing side, the support sleeve is provided with at least one projection which, viewed radially, projects from the outer edge of the support sleeve and, viewed axially, projects from the end face of the support sleeve on the valve housing side; the convex part is designed to be elastic when viewed in the radial direction and is embedded into the slot; in the locked position of the bayonet connection, the end of the projection engages in the associated recess.

The basic idea of the invention is that: in all the process valves of the type mentioned, which function as lift valves, i.e. single-seat valves and double-seat valves designed as shut-off valves, tank bottom valves, reversing valves or single-way valves, multi-way valves, the connection mentioned can be realized by means of a bayonet connection or bayonet-like connection which saves structural height. In this connection position, the complex closing mechanism, which is usually the case, can be dispensed with by means of a bayonet mechanism, so that the connection is simplified in terms of construction to a great extent according to the object of the invention.

A preferred embodiment of the bayonet connection provides for: the insulating body casing, which is preferably of tubular design, has at its end on the valve housing side at least two plug-in lugs projecting radially inward in the radial view on the insulating body side, which are each delimited on both sides by a plug-in recess which is formed between them on the insulating body side. The valve housing has a corresponding number of radially outwardly projecting detent lugs on one side of the valve housing, on the outside and in the circumferential region of the valve housing opening, which are each delimited on both sides by detent recesses formed between them on one side of the valve housing. The latching lugs on the side of the insulating body engage in the latching recesses on the side of the valve housing in an open position of the bayonet coupling, and they engage behind the latching lugs on the side of the valve housing in an almost overlapping manner in a closed position of the bayonet coupling.

If, as stated otherwise, two plug-in lugs are provided on the side of the insulating body, these lugs are diametrically opposite one another; alternatively, more than two latching lugs are provided on the side of the partition, which are distributed uniformly over the circumference of the tubular partition housing, so that the drive housing, together with a pressure medium connection arranged thereon, can be selectively rotated by 180 degrees or by a smaller angle (which can be determined from the number of latching lugs) relative to the valve housing in order to be fixed in those specific positions on the valve housing.

According to a further embodiment of the invention, the actuating rod is guided in a tubular support sleeve which is arranged and fixed in the insulating body casing and which makes full use of the axial length of the insulating body casing. This guiding of the actuating lever can therefore also be used at the same time for guiding the drive piston which is fixedly connected to the actuating lever. Since the actuating lever is fixedly connected to the blocking part, the latter is also guided axially indirectly via the bearing bush, so that no additional installation height in the overall installation range is required for this guide mechanism.

The function of the spacer housing, in addition to ensuring its mechanical connection function, also ensures that the valve housing and the actuator housing, which contain different and mutually incompatible fluids, are reliably separated, which function is not impaired by the mentioned support sleeve, since the latter has at least one support sleeve opening, viewed radially, through the wall of the shank of a tubular support sleeve.

In order to ensure the drainage of the leakage, another proposal is made: the at least one support sleeve aperture is at least partially overlapped by the at least one isolator aperture to allow fluid passage therethrough. The at least partial overlapping is ensured, for example, by a torsion-resistant device of the bearing bush in the insulator housing accommodating the bearing bush, for example, by a form-fitting connection or engagement. In this case, a bayonet lug which is inserted into the isolator housing and is located on the valve housing side is supported axially downward on the bearing sleeve.

The penetration point between the actuating rod and the valve housing requires a sealing measure in the region of the valve housing opening in question by means of a rod seal which, in the installed state, must be under sufficient radial pretension for a sufficient sealing effect. In the installed state, the radial pretensioning is produced only by a minimal axial deformation of the rod seal during the closing of the bayonet connection. In this way, the rod seal and the latch associated with its operating rod can be easily removed without the use of special tools. This is achieved according to an advantageous embodiment by the following measures: a bearing sleeve flange of the bearing sleeve on the side of the valve housing is supported on the valve housing which surrounds the valve housing opening on the outside, wherein the rod seal arranged between the valve housing opening and the actuating rod, the cross section of which is enlarged, is axially preloaded.

Since it cannot be ruled out that, in the operation of the poppet valve, liquid, product or cleaning agent, as seen from the interior of the valve housing, is brought to the sealing area, even behind the rod seal, by the so-called "lifter effect", care must be taken to: the entrained liquid can be discharged at least without pressure. The following settings were made for this: a plurality of grooves distributed over the circumference are embedded in the end face of the support sleeve on the valve housing side, which grooves penetrate the support sleeve at those locations, wherein the drainage through the bayonet connection is ensured radially on the outside.

According to a further advantageous embodiment, the bayonet connection or bayonet-like connection is automatically positively locked in its locking position. This locking is achieved by a number of measures, some of which are conditional on each other. On one hand, the following settings are made: the tubular isolator housing has a slot in the region of at least one circumferential projection on the side of the isolator, which slot extends axially into the end of the isolator housing on the side of the valve housing and extends radially through the isolator housing from the inside to the outside.

On the other hand, the following settings are made: each valve-housing-side bayonet-type lug has, radially on the outside, a groove-shaped recess which is limited in terms of its radial depth and its circumferential extent, wherein, in the closed position of the bayonet connection, the recess, viewed in the circumferential direction, is positioned in superimposition with the associated groove gap. In a preferred embodiment, the recess is arranged centrally, as viewed in the circumferential direction, on the associated detent flange on the valve housing side.

In addition, at least one projection is arranged on the support sleeve in the region of the valve-housing-side end of the support sleeve, which projection projects, on the one hand, from the outer edge of the support sleeve, viewed radially, and, on the other hand, projects, viewed axially, from the valve-housing-side end face of the support sleeve. The projection is designed to be elastic when viewed in the radial direction and engages in the associated slot. This ensures a rotationally fixed mounting of the bearing bush already described above in the insulator housing.

The automatic locking of the bayonet coupling, which simultaneously prevents its unintended opening, is achieved by the following measures: in combination with the features described above, in the closed position of the bayonet connection, the end of the projection engages in an associated groove-shaped recess in the latching flange on the valve housing side. The resilient design of the projection allows it to be bent radially outward from the open position of the bayonet connection, to the extent that it engages over the outer edge of the latching collar on the valve housing side in the latching position of the bayonet connection and is guided out circumferentially over the latching collar until it snaps into the groove-shaped recess in an inward, form-locking manner with its elastic return to the shape. In this way, a form-locking connection between the support sleeve and the support sleeve housing on the one hand and the valve housing on the other hand is ensured.

In addition, the invention also proposes: the features mentioned above can also be used for a shut-off valve; the valve housing is designed in the form of a first valve housing which functions as a valve housing of the shut-off valve.

Likewise, the features mentioned above can also be used for a tank bottom valve, according to which the second connecting pipe opens from below into the tank bottom of a tank or container; the valve housing is designed in the form of a second valve housing which functions as a can bottom valve housing.

Furthermore, the features mentioned above can also be used in a reversing valve in which the separator housing is connected to the valve housing part via a second valve housing part having at least one fourth connecting line, and in which case the valve housing is designed in the form of a third valve housing which functions as a reversing valve housing; in this valve, the two valve housing parts are connected via a second connecting opening, in or on which a second seat surface is formed. A second latch is fastened to the actuating lever, which latch interacts with the second seat surface via a radially acting second latch seal and controls the second connecting opening, wherein in the latched position of the second latch, the latch of the first latch assumes its associated open position; in the closed position of the first closure part, the second closure part assumes its associated open position. The third valve housing is changed for a large use of the proposed poppet valve into a through-type valve housing, if it is provided, as proposed, on the second valve housing part, in addition to the fourth connecting piece, also a fifth connecting piece, which is opposite the fourth connecting piece.

The valve housing of the above-mentioned shut-off valve, tank bottom valve and reversing valve can each be a through-type valve housing in the region of its housing part, also for the above-mentioned purposes, if it has, in addition to the first connecting line, a third connecting line, which is opposite the first connecting line.

Finally, the features mentioned above can also be used for a double seat valve with two parallel-arranged blocking parts which can be moved relative to one another and which, in the blocking position of the double seat valve, prevent fluid from flowing out of one valve housing part into the other valve housing part, which blocking parts delimit a leakage space which is connected to the environment of the double seat valve both in the blocking position and in the open position, and which double seat valve has a common servo drive on both blocking parts for a vertical arrangement, which drive its associated actuating lever.

A preferred development of the double seat valve provides that if a leak-free connection is desired or required: both latching sections are designed as sliding pistons which, in the latched position of the double seat valve, are supported in a sealing manner in a connecting opening which connects the two valve housing parts to one another and forms a cylindrical seat surface. The first closure part bears tightly against the second closure part during its opening movement before it leaves the cylindrical seat surface, and the second closure part is likewise guided into a fully open position during the further opening movement. The double seat valve opens upwards and has a discharge opening which is provided in a stem which is arranged on the first closing part and passes through the second valve housing part in a downward-sealing manner and connects the leakage chamber to the environment.

If necessary, the valve housing part of the double seat valve can be changed from the respective valve housing part to a through-opening valve housing, with the proviso that the valve housing part, in addition to the respective connecting piece, also has a further connecting piece, which is opposite the other connecting piece.

Drawings

A more complete understanding can be obtained from the following description and the accompanying drawings. The invention is achieved in a very different embodiment, and in the figures there is shown an embodiment of the preferred embodiment of the device according to the invention, which can be used for different valve types each operating as a poppet valve (stop valve as single-seat valve and double-seat valve; tank bottom valve and reversing valve as single-seat valve respectively), and which is explained below in terms of its structure and function, with the proviso that: this embodiment represents only one example of the invention, and the invention is not limited to the specifically illustrated example.

The attached drawings show that:

FIG. 1 is a general perspective view of a poppet valve of the present invention in a shut-off valve design;

fig. 2 is a longitudinal section through a preferred embodiment of the shut-off valve shown in fig. 1 in its closed position, provided with a spring-closed servo drive, the section plane being selected such that it passes through the spacer opening and the support sleeve opening, which overlap in this plane;

fig. 3a longitudinal section of the poppet valve proposed by the invention, according to the design as a double seat valve;

fig. 4 shows a longitudinal section through a poppet valve according to the invention, in a design as a switching valve, in which a uniform closing part which can be displaced in two switching positions and which has two selectable sealing positions arranged at a distance from one another is brought into the switching position above it by the pressure medium acting against the force of a drive spring; the cutting plane is selected such that it passes through a projection of a locking bayonet connection on a support sleeve;

fig. 5 shows a longitudinal section through a lift valve according to the invention, designed as a tank bottom valve, wherein, in the closed position shown, a spring-closed servo drive closes a tank bottom opening with the closing part; the cutting plane is also selected such that it passes through the superimposed openings of the spacer and the support sleeve in the cutting plane;

FIG. 6 is a perspective view of an embodiment of an isolator housing having an actuator-side isolator flange on one end thereof, the isolator flange bounding an actuator housing of a servo actuator on a valve housing side; on its other end, one half of a bayonet lock is shown;

fig. 7 is a perspective view of an embodiment of the valve housing, wherein the complementary other half of the bayonet lock shown in fig. 6 is visible on the upper side;

fig. 8 is a first perspective view of an embodiment of a bearing sleeve, which is complementary to the insulator housing shown in fig. 6, the view being on the longitudinal side and on a projection for the locking of the bayonet lock;

fig. 9 is a perspective view of the support sleeve of fig. 8, from a lower perspective.

Detailed Description

A poppet valve 1 (fig. 1) according to the invention designed as a shut-off valve 1.1 essentially comprises: a valve housing 2 (shut-off valve housing) in the form of a first valve housing 2.1, which comprises, for example, a central, preferably conically designed housing part 2a, a first connecting pipe 2b branching off laterally and a second connecting pipe 2c branching off downwardly for the position shown (see also fig. 7). It also comprises a first spring-closed servo drive 3 (fig. 2) or a second spring-open servo drive 3^＊In the case of the servo drive, a drive piston 5 passes through a first or second pressure medium port 3e or 3e, respectively, which is formed in a drive housing 3a^＊(Servo driver 3)^＊) Usually with a gaseous pressure medium D (compressed air). Servo driver 3, 3^＊Is carried out via a first venting opening 3d in a venting plug 14 (fig. 1) or via a second venting opening, not shown, in a second, likewise not shown, venting plug on the side of the drive piston 5 which is subjected to a pressure during the opening and closing movement. Servo driver 3, 3^＊In addition to the spring-closed or spring-open embodiments described above, there are also embodiments of a dual-action design. This embodiment, which is described below, is likewise not shown in the figures, and, in addition to other variants of this servo drive, which are not described here, it also has a further pressure medium opening on the other side of the drive piston 5 on the drive housing 3 a. In addition to the first connecting pipe 2b, the valve housing part 2a may also have a third connecting pipe 2b^＊Since this connecting pipe faces the first connecting pipe 2b, the valve housings 2, 2.1 form a through valve housing.

In the valve housing 2, 2.1 (fig. 2), a connecting opening 2d is arranged between the two connecting lines 2b, 2c, in or on which a seat surface 2e is formed. A lock 4 movable toward the servo driver 3 engages the seat surface 2e and controls the connection orifice 2 d. An actuating rod 4a/4b is fastened to the closing part 4, is guided out of the valve housing 2, 2.1 in a sealing manner via a housing opening 2h opposite the connecting opening 2d and interacts with the servo drive 3, 3^＊The drive piston 5 of (a) is fixedly but detachably connected. Servo driver 3, 3^＊In the drive housing 3a there is a drive piston 5 which is movable against the force of the drive spring 7 or 7.1, 7.2 and is loaded with a pressure medium D. The actuating lever 4a/4b is enlarged in its cross-section at least in its passage area with the valve housing 2, 2.1 in such a way that it receives the drive spring 7 and 7.1, 7 in a pot-shaped recess 4c there2a portion on the latch side.

Valve housing 2, 2.1 and pneumatic servo drive 3, 3^＊Are directly connected to each other via an isolator housing 3.1. The servo drives 3, 3 arranged on the isolator housing 3.1^＊An isolator flange 3.1a (see also fig. 6) on the side of the drive forms the boundary of the drive housing 3a on the side of the valve housing. Servo driver 3, 3^＊On its side facing away from the valve housing 2, 2.1, it is closed by a cover part 3b (fig. 2, 1) which extends externally and centrally in a clamping flange 3f of smaller diameter and is centrally connected by a response rod 16, preferably detachably connected to the actuating rod 4a/4b, or a modified response rod 17 (servo drive 3)^＊) And (4) penetrating. In the simplest case, either the upper end of the response rod 16, 17 indicates the relevant position of the poppet valve 1 optically, or the upper end is detected in a contact or contactless manner and fed back via a control head arranged on the clamping flange 3f to an internal or external control device which controls the poppet valve 1.

The isolator housing 3.1 (fig. 6) has a tubular isolator shank 3.1b, which is provided at one end with an isolator flange 3.1a on the driver side and at the other end with means 3.1d, 3.1e for connecting the isolator housing 3.1 to the valve housing 2, 2.1, and two isolator orifices 3.1c which are arranged radially in the isolator shank 3.1b and pass through the shank. The means 3.1d and 3.1e are designated a card flange 3.1d on the side of the insulating body and a card recess 3.1e on the side of the insulating body. The two spacer openings 3.1c are at least partially overlapped by three support sleeve openings 6c (fig. 8, 9) in a support sleeve 6 (fig. 1), through which openings 3.1c, 6c a connection is made between the circumference of the shut-off valve 1.1 and an operating rod 4a, a so-called pressure compensation piston, whose cross-section is enlarged (see also fig. 2). The support sleeve opening 6c is formed in a tubular support sleeve shank 6a of the support sleeve 6, wherein the support sleeve shank 6a merges at its lower end into a radially outwardly projecting support sleeve flange 6b on the valve housing side.

At the lower end of the valve housing 2, 2.1 (fig. 2), above the second connecting pipe 2c which delimits the connecting opening 2d, for example, to a leading pipe, not shown in the drawing, or to a tank body, a seat surface 2e is formed on the inner wall of the central valve housing part 2a concentrically to the vertical axis of symmetry of the latter, which seat surface is designed in the present embodiment as a cylinder; on this seat surface, the closure 4 designed as a sliding piston is supported in a sealing manner with its closure seal 9. The closure seal 9 acts purely in radial cooperation with the cylindrical seat surface 2 e; the blocking position of the shut-off valve 1, 1.1 is then preferably established by means of the actuator 3, 3^＊Preferably, a fixed stop of the drive piston 5 is limited by a stop on the isolator flange 3.1a on the side of the drive.

It is also proposed that the closure 4 be designed as a seat disk with an axially or axially/radially acting closure seal 9, which seat disk interacts with an associated seat surface 2e, which is designed axially or conically, and that the closure position of the shut-off valve 1, 1.1 be limited by a fixed stop of the closure 4 on the respective seat surface.

The closing part 4 merges at the top into a connecting rod 4b (fig. 2) of reduced cross section, which on the other hand widens into an actuating rod 4a of enlarged cross section, which is designed for a pressure compensation piston. In order to compensate for pressure surges in the interior of the valve housing 2, 2.1, the closing part 4 is therefore assigned a counter-pressure surface 4g in the transition region to the operating rod 4b of reduced cross section at the operating rod 4a of enlarged cross section. The actuating rod 4a, which is enlarged in cross section, extends with a non-narrowing cross section up to the drive piston 5 and is connected fixedly, but detachably, to the drive piston on its rod end 4e, which is on the drive side and is preferably designed as an external thread. The actuating rod 4a, which is enlarged in cross section, passes through the central valve housing part 2a in the upper valve housing opening 2h (see also fig. 7 for this purpose), wherein the sliding passage is sealed by means of a rod seal 10 which is arranged in the valve housing opening 2 h.

The actuating lever 4a/4b with the latch 4 is guided in a tubular support sleeve 6 which is arranged and fixed in the insulator housing 3.1, making full use of the axial length of the insulator housing. The housing-side housing flange 6b of the housing 6 is supported on the housing 2, 2.1 which surrounds the housing opening 2h on the outside and axially pretensions the rod seal 10 which is arranged between the housing opening 2h and the actuating rod 4a whose cross section is enlarged. The stem seal 10 is embedded in an annular recess in an annular nipple 2i into which the upper end of the valve housing part 2a engages (fig. 7). A plurality of grooves distributed over the circumference are embedded in the end face of the support sleeve 6 on the valve housing side, which grooves penetrate the support sleeve 6 at those locations. These grooves serve the purposes mentioned hereinbefore.

Above the bearing bush 6, the actuating rod 4a, which is enlarged in cross section, passes through a drive-side isolator flange 3.1a in a through-opening 3.1f (fig. 6, 2), wherein this passage is sealed by a first seal 11 of the drive housing 3 a. This first seal 11 ensures: no pressure medium D can escape from the cavity formed between the bearing bush 6 and the actuating rod 4a, the cross section of which is enlarged, and which is fed in the stroke through the first pressure medium opening 3e into the cavity formed between the underside of the drive piston 5, the drive housing 3a and the isolator flange 3.1a on the drive side. The sealing of the driver-side isolator flange 3.1a with respect to the driver housing 3a is effected via a second seal 12, whose fixing in the driver housing 3a is effected via a safety ring 13. The drive piston 5 is sealed in a sliding manner with respect to the inner circumferential surface of the drive housing 3a by means of an unmarked piston seal.

On the actuating lever 4a, the cross-section of which is enlarged, a pot-shaped recess 4c is provided, which, viewed in cross-section, is situated in the region of the leverThe actuator-side rod end 4e extends, without narrowing, to the lower end of the actuating rod 4a, the cross section of which is enlarged. In this case, the actuation lever 4a, which is enlarged in cross section in the closed position of the shut-off valve 1.1, projects into the valve housing part 2a at least by a full valve stroke H (fig. 2), so that in the open position of the shut-off valve 1.1 open toward the servo drive 3, i.e. after completion of the full valve stroke H, the lower end of the actuation lever 4a, which is enlarged in cross section, still obtains a radial seal with respect to the lever seal 10 (see also fig. 4). A bowl bottom 4f or 4f of the bowl-shaped recess 4c^＊For the drive spring 7 or 7.1, 7.2, which is preferably designed as a helical spring, it is possible to have more than one drive spring in the form of a spring pack 7.1, 7.2, the pot base serving as the movable spring support 4d on the latch side. The drive spring 7 or 7.1, 7.2 is supported on the other hand on the cover 3b of the actuator 3, wherein a circular recess, not shown, is preferably provided for the central fastening of the drive spring 7 or 7.1, 7.2. The cover part 3b thus forms an immovable spring support 3c on the drive side.

In order to meet the US requirements with respect to the previously mentioned 3-A sanitary standards for valves of the compression type, these standards also require servo drives 3, 3^＊It must be easily detachable from the valve housings 2, 2.1 and the actuating levers 4a/4b of the blocking part 4, so that the actuating levers 4a/4b are detachably connected (fig. 2). This division is preferably realized in the region of the actuating lever 4a with an enlarged cross section, i.e. into an actuating lever part 4a on the latch side^＊And a lever portion 4a on the driver side^＊＊. The two lever portions 4a^＊、4a^＊＊A form-and force-locking connection sealed by a third seal 15, via the part 4a on the side of the closure^＊Upper internal thread 4a.1^＊And a portion 4a at one side of the driver^＊＊External thread 4a.1 on^＊＊And then the implementation is realized. A lever portion 4a on the driver side^＊＊Extending into a bowl at the end of the lock partBody 4a.2^＊＊The bowl being embedded in an operating lever part 4a on the side of the latch^＊And a second bowl bottom 4f is formed at the position^＊The bowl-shaped recess 4 c. Thus, when the operating lever 4a with its cross section enlarged is divided into two parts, a lower part 4a^＊It is left on the latch 4 by the connecting rod 4b of reduced cross section; an upper part 4a^＊＊Is fixedly but detachably connected to the drive piston 5. Bowl 4a.2^＊＊Which has on the inside the contour of the pot-shaped recess 4c, which, as defined in the non-segmented embodiment, prevents the segment 4a from being segmented^＊、4a^＊＊The preloaded drive spring 7 or 7.1, 7.2 arranged in the pot can relax uncontrollably.

Servo driver 3.3 associated with isolator housing 3.1 on one side of housing 2, 2.1^＊For a form-locking and force-locking connection between the other side, a bayonet-type connection 2f, 2g/3.1d, 3.1e or a bayonet-like connection (fig. 1 in conjunction with fig. 2, 6, 7) is provided. For this purpose, the isolator housing 3.1 (fig. 6) has at its end on the housing side at least two spacer-side detent lugs 3.1d projecting radially inward, viewed radially, which are each delimited on both sides by detent recesses 3.1e formed between them on the spacer side. The valve housing 2, 2.1 (fig. 7) has, on the outside and in the circumferential region of the valve housing opening 2h, a corresponding number of valve housing-side detent lugs 2f which project radially outward, as viewed radially, and which are each delimited on both sides by a valve housing-side detent recess 2g formed between them. The plug-in flange 3.1d on the side of the isolating body engages in the plug-in recess 2g on the side of the valve housing in the open position of the bayonet coupling; in the closed position of the bayonet connection, however, they engage behind the latching flange 2f (bayonet closure 2f/3.1d) on the valve housing side almost in superposition.

The two housing-side bayonet lugs 2f are preferably arranged on the housing part 2a offset by 90 ° in relation to the first connecting pipe 2b, so that the preferably material-bonded split connection between the first connecting pipe 2b and the housing part 2a, which is usually produced by machine-track welding, is not impeded by these housing-side bayonet lugs 2 f. The latching recesses 2g on the valve housing side engage radially on the inside up to the annular connecting piece 2 i. In the exemplary embodiment shown, two radially arranged, housing-side latching lugs 2f and two corresponding housing-side latching recesses 2g together form part of a bayonet connection 2f, 2g/3.1d, 3.1 e. Two radially arranged plug-in lugs 3.1d on the insulator side and two plug-in recesses 3.1e on the insulator side form a further part of the bayonet connection 2f, 2g/3.1d, 3.1 e. Another advantageous embodiment of the bayonet connection 2f, 2g/3.1d, 3.1e provides for more than two detent lugs 3.1d on the insulator side, which are distributed uniformly over the circumference of the tubular insulator housing 3.1. The parts 2f, 2g of the bayonet connection on the valve housing side are in this case designed complementarily.

The bayonet connections 2f, 2g/3.1d, 3.1e or bayonet-like connections automatically lock in a form-locking manner in their closed position (fig. 1, 4, 6, 7). For this purpose, the tubular insulator housing 3.1 or its tubular insulator shank 3.1b has a groove 3.1g (fig. 6, 1) in the region of at least one insert flange 3.1d on the insulator side with respect to the circumference, which groove extends axially into the insulator from the valve housing-side end of the insulator housing 3.1 and, in this case, extends through from the inside to the outside, viewed radially.

Each valve-housing-side detent flange 2f has, radially on the outside, a groove-shaped recess 2k (fig. 7) which is limited in its radial depth and its circumferential extension, wherein, in the closed position of the bayonet connection, the recess 2k, viewed in the circumferential direction, is positioned in superimposition with the associated groove gap 3.1 g. The recess 2k is preferably arranged centrally in the circumferential direction on the associated detent flange 2f on the valve housing side.

In the end region of the support sleeve 6 on the valve housing side, at least one projection 6d (fig. 8, 9, 4, 1) is arranged on the support sleeve, which projection, viewed radially, projects from the outer edge of the support sleeve 6; on the other hand, it projects from the end face of the support sleeve 6 on the valve housing side, as viewed in the axial direction. The projection 6d is designed to be elastic, viewed in the radial direction, and engages in the associated recess 3.1g (fig. 1), so that a defined fixing of the bearing bush 6 in the insulator housing 3.1 is ensured in the circumferential direction.

In order to achieve an automatic form-locking of the bayonet connection 2f, 2g/3.1d, 3.1e, the following is provided: in the locked position of the connection, the end of the projection 6d engages in the associated recess 2k (fig. 4).

The above-described features of the poppet valve 1 according to the invention can also be used advantageously in a reversing valve 1.3 (fig. 4) in which the isolator housing 3.1 is connected via a fourth connecting line 2b having at least one^＊＊Of the second valve housing part 2a^＊And to the valve housing part 2a, so that the valve housing 2, 2.3 is designed in the form of a third valve housing 2.3 functioning as a reversing valve housing. Two valve housing parts 2a, 2a^＊Through a second connecting aperture 2d^＊And a second seating surface 2e of cylindrical configuration is formed in or on the connecting opening^＊. A second closure 4.2 is additionally fastened to the actuating lever 4a/4b in the region of the actuating lever 4b, the cross section of which is reduced, via a second radially acting closure seal 9^＊And is fitted with the second seating surface 2e^＊Act together and control the second connecting orifice 2d^＊. In the closed position of the second latch 4.2, the latch 4 forming a first latch 4.1 assumes its associated open position; in the closed position of the first latch 4.1, the second latch 4.2 assumes its associated open position.

If necessary, can be selected fromThe valve housing part 2a becomes a through valve housing with the proviso that the valve housing has to have a third connecting pipe 2b in addition to the first connecting pipe 2b^＊Which is opposite to the first connection tube 2 b. Likewise, if necessary, from the second housing part 2a^＊A through valve housing is formed, with the proviso that the valve housing has a fourth connecting tube 2b in addition^＊＊In addition, a fifth connecting tube 2b must be provided^＊＊＊Which is opposite to the fourth connecting tube 2b^＊＊。

With such an arrangement, a reversing function is achieved, wherein in the upper position of the illustrated closure 4, i.e. where its second closure 4.2 assumes a closure position, in the first and possibly third connecting pipe 2b or 2b^＊A connection is established between one side and the second connecting tube 2c as the other side. In the lower position of the closure 4, i.e. where its first closure 4.1 assumes a closure position, the fourth and possibly fifth connecting piece 2b^＊＊Or 2b^＊＊＊One side of which is connected to the first and possibly third connecting tube 2b or 2b^＊Is connected with the other party.

According to another proposal, the aforementioned features of the proposed poppet valve 1 can also be used in a tank bottom valve 1.2 (fig. 5), in which the second connecting line 2c opens from below into the tank bottom 2l of a tank or container, the valve housing 2, 2.2 being designed in the form of a second valve housing 2.2 which functions as a tank bottom valve housing. From the latter, if appropriate, a through-valve housing can also be formed, with the proviso that the valve housing has a third connecting line 2b in addition to the first connecting line 2b on the valve housing part 2a^＊Which is opposite to the first connection tube 2 b.

Finally, the aforementioned features of the poppet valve 1 according to the invention can also be advantageously used in a double seat valve 1.4 (fig. 3), in which the spacer housing 3.1 is connected to an upper housing part 2.4a having at least one first pipe connection 2.4c and a second connecting pipe 2 c. Here, the upper valve housing part 2.4a corresponds to the aforementioned valve housing part 2a, and the first pipe connector 2.4c corresponds to the aforementioned first connecting pipe 2 b. Between the first pipe connection 2.4c and the second connection pipe 2c, a connection opening 2d is arranged in the upper valve housing part 2.4a, in or on which a seat surface 2e is formed. Opposite the connection opening 2d is a valve housing opening 2h, through which access to the servo drive 3 is made available during travel via the isolator housing 3.1. Here, this valve housing structure corresponds to any of the above-described structures in the poppet valve 1 that operates as a single seat valve. The second connecting line 2c, which surrounds the connecting opening 2d, connects the upper valve housing part 2.4a to a lower valve housing part 2.4b, which opens into at least one second pipe connection 2.4d, whereby the valve housings 2, 2.4 are in the form of a fourth valve housing 2.4 which functions as a double-seat valve housing.

On the outer circumference of the connection opening 2d, which connects the two valve housing parts 2.4a, 2.4b to one another, a cylindrical seat surface 2e is provided, which interacts with an independently driven first latching means 20 and an independently driven second latching means 21, which is arranged above it for the vertical normal position. The two closure parts 20, 21 are designed as so-called sliding pistons, each of which is provided with a radial sealing mechanism (seal in so-called sliding engagement), wherein the first closure part 20 has a first closure part seal 23 on its cylindrical circumferential surface and the second closure part 21 has a second closure part seal 24 on its cylindrical circumferential surface.

During the opening movement of the double seat valve 1.4, the first latch 20 first comes to bear against an intermediate seal 25, which is arranged on the front face of the second latch 21, after a partial lift, so that during the further opening movement the two latches 20, 21 are brought into their fully open position. Between the two locking parts 20, 21, in both the locking position and the open position, there is a leakage space 22 which is connected to the environment of the double seat valve 1.4 via a discharge opening 20 c. The outlet bore 20c extends coaxially through a tubular shank in the form of a pressure compensation piston 20b, which is connected to the first closing part 20 and is led out downwards through the lower valve housing part 2.4 b.

The first latch 20 is connected on the upper side to a first actuating lever 20a, which is introduced into the servo drive 3, not shown in detail, which is arranged above the second valve housing part 2.4 a. The second latch 21 extends upwards into a second actuating rod 21a, which is designed as a second pressure compensation piston and which surrounds the first actuating rod 20a concentrically in the form of a hollow rod and is also introduced into the servo drive 3. The actuator 3, which is preferably a piston/spring-type actuator acted on by a pressure medium, is normally capable of both opening and closing movements of the closure parts 20, 21, and also of the respective partial lifting movements of the two closure parts, which are independent of one another, during the so-called cleaning of the support.

If appropriate, the valve housing parts 2.4a, 2.4b can each be a through-opening valve housing, with the proviso that the valve housing parts 2.4a, 2.4b have, in addition to the associated pipe connections 2.4c, 2.4d, a further pipe connection which is opposite the other pipe connections.

Concerning the following design: isolator housing 3.1; a bearing sleeve 6 mounted in the isolator housing, which guides the second actuating lever 21a and seals the second actuating lever 21a in conjunction with the lever seal 10 against the upper housing part 2.4 a; the mounting and fixing of the isolator housing 3.1 on the actuator housing 3a via the isolator flange 3.1a on the actuator side is designed exactly the same as the corresponding structural component on a poppet valve 1 of the type described above, which works as a single seat valve. This conclusion also relates to the device according to the invention in the form of the bayonet lock 2f/3.1d described above and to various modifications and improvements thereof.

From the foregoing, it will be observed that numerous modifications and variations can be effectuated without departing from the true spirit and novel designs of the present invention. This must be understood as follows: the embodiments of the device are illustrated and described herein, or merely stated, without intending to be limited to the described embodiments. The disclosure is intended to embrace all such modifications/variations as fall within the scope of the appended claims.

List of reference numerals

1 lift valve (Overall)

1.1 stop valve

1.2 reversing valve

1.3 tank bottom valve

1.4 double seat valve

2 valve casing (Overall)

2a valve housing part

2b first connecting pipe

2c second connecting pipe

2d connecting orifice

2e seat surface (Cylinder shape; taper shape, axial)

2f card-insertion flange at one side of valve casing

2g card-inserting recess on one side of valve casing

2h valve housing orifice

2i annular connecting pipe

2k trough-shaped recess

Cut-off valve (1.1)

2.1 first valve casing (cut-off valve casing)

2b^＊Third connecting pipe

Tank bottom valve (1.2)

2.2 second valve casing (tank bottom valve casing)

2b^＊Third connecting pipe

2l tank bottom

Reversing valve (1.3)

2.3 third valve casing (reversing valve casing)

2a^＊Second valve housing portion

2b^＊Third connecting pipe

2b^＊＊Fourth connecting pipe

2b^＊＊＊Fifth connecting pipe

2d^＊Second connecting orifice

2e^＊(cylindrical) second seat surface

4.1 first latch

4.2 second latch

9^＊Second closure seal

＊＊＊

3 driver (spring switch; spring switch)

3a driver housing

3b cover part

3c spring support on the driver side

3d exhaust vent

3e pressure medium orifice

3e^＊Second pressure medium port

3f clamping flange

3.1 isolator Shell

3.1a isolator flange on driver side

3.1b tubular separator shank

3.1c isolator ports

3.1d card insertion flange on one side of the isolator

3.1e card-insertion recess on one side of the isolator

3.1f outer casing ring

3.1g of slot

2f, 2g/3.1d, 3.1e bayonet type connecting mechanism

2f/3.1d bayonet type locking body

4 locking part (Overall)

4a/4b joystick

4a operating rod with enlarged cross section (pressure balance piston)

4b Joystick with reduced cross-section

4c bowl-shaped recess

4d spring support on the side of the latch

4e connection terminal

4f bowl bottom

4f^＊Second bowl bottom

4g counter pressure surface

4a^＊Lower part of pressure balance piston

4a^＊＊Upper part of pressure balance piston

4a.1^＊Internal screw thread (in the lower part 4a)^＊Upper)

4a.1^＊＊External screw thread (at the upper part 4a)^＊＊Upper)

4a.2^＊＊Bowl body

5 drive piston

6 support sleeve

6a support sleeve handle

6b supporting sleeve flange

6c support sleeve orifice

6d convex part

7 drive spring

7.1 first drive spring

7.2 second drive spring

9 closure seal

10-bar seal

11 first seal (driver outer cover)

12 second sealing piece (driver outer cover)

13 safety ring

14 air-out plug

15 third sealing element (pressure balance piston)

16 responsive rod

17 modified response rod

Double-seat valve (1.4)

2.4 fourth valve casing (double-seat valve casing)

2.4a Upper valve housing portion

2.4b lower valve housing part

2.4c first pipe joint

2.4d second pipe joint

20 first latch part

20a first operating lever

20b first pressure balanced piston

20c discharge hole

21 second latch portion

21a second control rod (second pressure balance piston)

22 leakage cavity

23 first closure seal

24 second closure seal

25 middle seal

＊＊＊

D pressure medium

H (full) valve lift; fully open position

Claims (18)

1. A process valve functioning as a lift valve (1; 1.1; 1.2; 1.3; 1.4) has: a valve housing (2; 2.1; 2.2; 2.3; 2.4) comprising at least one valve housing part (2 a; 2.4 a; 2.4 b); at least one first and one second connection pipe (2b, 2 c; 2.4c, 2c) which are connected to the valve housing part (2 a; 2.4 a; 2.4b) and which establish a communication to the interior of the valve housing part; a connecting opening (2d) which is arranged in the valve housing (2; 2.1; 2.2; 2.3; 2.4) between the connecting tubes (2b, 2 c; 2.4c, 2c) and in which or on which at least one seat surface (2e) is formed; at least one translationally movable closure (4; 4.1; 21) which interacts with the associated seat surface (2e) and controls the connection opening (2 d); a control rod (4a/4 b; 21a) which is fastened to any of the locking parts (4; 4.1; 21) and which is guided out of the valve housing (2; 2.1; 2.2; 2.3; 2.4) in a sealing manner via a valve housing opening (2h) of the valve housing opposite the connecting opening (2d) and is connected to a drive piston (5) of a servo drive (3); an isolator housing (3.1) connecting the valve housing (2; 2.1; 2.2; 2.3; 2.4) to the actuator (3), said isolator housing having means (2f, 2g/3.1d, 3.1e) for connection to the valve housing (2; 2.1; 2.2; 2.3; 2.4) at least at its end on the side of the valve housing,

the method is characterized in that:

the isolator housing (3.1) is fixed on the valve housing (2; 2.1; 2.2; 2.3; 2.4) by a bayonet type connecting mechanism (2f, 2g/3.1d, 3.1 e);

the housing (3.1) of the separating body has at its end on the housing side at least two plug-in lugs (3.1d) projecting radially inward in the radial direction on the side of the separating body, which are each delimited on both sides by a plug-in recess (3.1e) formed between them on the side of the separating body; the valve housing (2; 2.1; 2.2; 2.3; 2.4) has, on the outside, in the circumferential region of the valve housing opening (2h), a corresponding number of valve housing-side plug-in lugs (2f) which project radially outward in the radial direction and which are each delimited on both sides by a valve housing-side plug-in recess (2g) formed therebetween, wherein the plug-in lug (3.1d) on the isolator side engages in the valve housing-side plug-in recess (2g) in the open position of the bayonet coupling and engages behind the valve housing-side plug-in lug (2f) in the closed position of the bayonet coupling in an almost overlapping manner;

and the bayonet connection (2f, 2g/3.1d, 3.1e) is automatically locked in a form-locking manner in the locking position thereof;

the separator housing (3.1) has a slot (3.1g) in the region of at least one plug-in flange (3.1d) on the separator side, which extends in a circumferential direction, starting from the valve housing-side end of the separator housing (3.1), a section which extends axially into the separator housing and, viewed radially, extends through from the inside to the outside;

each valve-housing-side detent flange (2f) has, radially on the outside, a groove-shaped recess (2k) which is limited in its radial depth and its circumferential extent, wherein, in the locked position of the bayonet connection, the recess (2k), viewed in the circumferential direction, is positioned in superimposition with the associated groove gap (3.1 g);

the actuating lever (4a/4 b; 21a) is guided in a tubular support sleeve (6) which is arranged inside the spacer housing (3.1) and is fixed and which makes the most of the axial length of the spacer housing; in the end region of the support sleeve (6) on the valve housing side, at least one projection (6d) is provided on the support sleeve, which projection projects from the outer edge of the support sleeve (6) when viewed radially and projects from the end face of the support sleeve (6) on the valve housing side when viewed axially; the raised part (6d) is designed to be elastic when viewed in the radial direction and is embedded into the corresponding slot (3.1 g);

in the locked position of the bayonet connection, the end of the projection (6d) engages in the associated recess (2 k).

2. The process valve of claim 1, wherein: two plug-in lugs (3.1d) are provided on the side of the insulating body, which are diametrically opposite one another.

3. The process valve of claim 1, wherein: more than two detent lugs (3.1d) are provided on one side of the insulating body, which are distributed uniformly over the circumference of the tubular insulating body housing (3.1).

4. The process valve of claim 1, wherein: the bearing bush (6) has at least one bearing bush opening (6c) through the wall thereof, viewed radially.

5. The process valve of claim 4, wherein: the at least one bearing sleeve opening (6c) is at least partially overlapped by at least one spacer opening (3.1c) allowing the passage of a fluid.

6. The process valve of claim 1, wherein: a housing-side housing flange (6b) of the housing (6) is supported on the housing (2; 2.1; 2.2; 2.3; 2.4) which encloses the housing opening (2h) on the outside, wherein a rod seal (10) arranged between the housing opening (2h) and the actuating rod (4a/4b) is axially prestressed.

7. The process valve of claim 1, wherein: a plurality of circumferentially distributed grooves are embedded in the end face of the support sleeve (6) on the valve housing side, said grooves extending continuously through the support sleeve (6) at those locations.

8. The process valve of claim 1, wherein: the recesses (2k) are arranged centrally in the associated plug-in flange (2f) on the valve housing side, as seen in the circumferential direction.

9. The process valve of any of claims 1-8, wherein: the features are used for a shut-off valve (1.1), and the valve housing (2; 2.1) is designed in the form of a valve housing which functions as a shut-off valve housing.

10. The process valve of any of claims 1-8, wherein: the features are used for a tank bottom valve (1.2), wherein the second connecting pipe (2c) opens from below into the tank bottom (2l) of a tank, and the valve housing (2; 2.2) is designed in the form of a valve housing which functions as a tank bottom valve housing.

11. The process valve of any of claims 1-8, wherein: each of the features is a reversing valve (1.3), wherein the separator housing (3.1) is connected to the valve housing part (2a) via a second valve housing part (2a) having at least one fourth connecting piece (2b), so that the valve housing (2; 2.3) is designed in the form of a valve housing acting as a reversing valve, wherein the two valve housing parts (2a, 2a) are connected via a second connecting opening (2d) in or on which a second abutment surface (2e) is formed, wherein a second latching part (4.2) having a second latching part seal (9) is additionally fastened to the actuating lever (4a/4b) and cooperates with the second abutment surface (2e) and controls the second connecting opening (2d), in the closed position of the second latch (4.2), the latch (4) forming a first latch (4.1) assumes its respective open position, and in the closed position of the first latch (4.1), the second latch (4.2) assumes its respective open position.

12. The process valve of claim 11, wherein: the valve housing (2; 2.3) has, on the second valve housing part (2a), in addition to the fourth connection (2b), a fifth connection (2b) which is opposite the fourth connection (2 b).

13. The process valve of claim 9, wherein: the valve housing (2; 2.1; 2.2; 2.3) has a third connecting piece (2b) on the valve housing part (2a) in addition to the first connecting piece (2b), which third connecting piece is opposite the first connecting piece (2 b).

14. The process valve of claim 10, wherein: the valve housing (2; 2.1; 2.2; 2.3) has a third connecting piece (2b) on the valve housing part (2a) in addition to the first connecting piece (2b), which third connecting piece is opposite the first connecting piece (2 b).

15. The process valve of claim 11, wherein: the valve housing (2; 2.1; 2.2; 2.3) has a third connecting piece (2b) on the valve housing part (2a) in addition to the first connecting piece (2b), which third connecting piece is opposite the first connecting piece (2 b).

16. The process valve of any of claims 1-8, wherein: each feature is used for a double seat valve (1.4) having two locking parts (20, 21) which are arranged in series and are movable relative to one another and which, in the locking position of the double seat valve (1.4), prevent the flow of fluid from one valve housing part (2.4 a; 2.4b) into the other valve housing part (2.4 b; 2.4a) from flowing out into the other valve housing part, wherein the locking parts, both in the locking position and in the open position, delimit a leakage cavity (22) which is connected to the environment of the double seat valve (1.4), and wherein, in the vertical arrangement, the double seat valve has a servo drive (3) which is common to both locking parts (20, 21) and which drives the respective actuating lever (20a, 21a) thereof.

17. The process valve of claim 16, wherein: two latching means (20, 21) are designed as sliding pistons, which are accommodated in a sealing manner in a connecting opening (2d) which connects the valve housing parts (2.4a, 2.4b) to one another and forms a cylindrical seat surface (2e) in the closed position of the double seat valve (1.4); the first closure (20) rests in a sealing manner against a second closure (21) during the opening movement thereof, before it leaves the cylindrical seat surface (2e), the second closure also being moved into a fully open position (H) during the further opening movement; the double seat valve (1.4) is open at the top and has a discharge opening (20c) which is arranged in a pipe shaft (20b) which is arranged on the first closure part (20) and passes through the second valve housing part (2.4b) in a downward-sealing manner and connects the leakage cavity (22) to the environment of the double seat valve (1.4).

18. The process valve of claim 16, wherein: the valve housing parts (2.4a, 2.4b) have opposite connecting pieces, so that a through-valve housing is formed in each case.