• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a closure device for industrial valves, with a plate or cover (12) for sealing an opening for a flow of fluid, and a sealing seat, the seal (12) being arranged between the sealing seat and a support device for applying to the cover (12) a bearing force, the support device comprising, in a casing (10), a plurality of pistons (48) and a transmission element for the transmission of the bearing force to the cap (12), which is arranged between the pistons (48) and the cap (12) and extends along the periphery of the cap, and the pistons (48). ) being connected to each other in fluid communication by a supply line (49) for a hydraulic fluid. The invention also relates to a valve with a single cap with such a closure device.
    公开号:FR3025277A1
    申请号:FR1557904
    申请日:2015-08-25
    公开日:2016-03-04
    发明作者:Robert Putz；Ingo Wirtz
    申请人:Z&J Technologies GmbH；
    IPC主号:
    专利说明:

    [0001] The invention relates to a closure device for industrial valves industrial facilities, including chemical and petrochemical plants, which interrupts a flow of fluid using a plate and has a seat of sealing, and which comprises in particular a cap for closing an opening for a fluid flow, and a sealing seat. The invention also relates to a plate valve or cap for chemical and petrochemical installations, with a casing which comprises a closable guide tube and a plate such as a cap capable of being moved to an open position and to a position closure and vice versa, a sealing seat being associated with the guide tube, which seat extends along the periphery of the guide tube and, in operation at least in the closed position, sealing from above against the operculum. Such a closure device and such a gate valve are known for example from WO 02/072729 A1. Such gate valves are used in the chemical and petrochemical industry, especially in coke plant installations. . In such facilities, residues from the oil refinery are processed. A preferred method for this is the so-called "delayed coking" process whereby the residues to be treated are converted into a coking drum (coke drum) into petroleum coke or into liquid or gaseous hydrocarbons. The treatment in the coking drum is carried out at a pressure of about 3 to 8 bar and at a temperature of about 500 ° C. The petroleum coke is cured with water vapor and water and is then cut into the coker drum with a water jet. During the reaction, the coker drum is closed. For cutting petroleum coke, the drum is open. Opening the drum is dangerous since hot, flammable gases can escape. For this reason, the opening of the coking drum, called "De-Heading", is performed automatically. For this purpose, valves are used which are connected to a corresponding opening of the drum and close or open it. Due to high process temperatures and pressures, the valves must be adequately sealed.
    [0002] For trouble-free operation, the valves must be easy to operate. We differentiate between single-gate valves and double-seal valves. The double-seal valves comprise two operculcles parallel to each other and spaced from one another, which are spaced apart by a wedge mechanism. In the closed position, this generates a significant sealing force which makes safe and reliable operation of the double seal valves possible. Single-gate valves have a simpler structure and are less high. They include prestressed sealing systems that provide the necessary sealing force. Such a valve to a single seal and, more generally, such a closure device are for example known from WO 02/072729 A1 mentioned above. The valve with a single known seal, or respectively the known closure device 10, comprises a lid in one piece, at the distal end of which is formed a tube bridge by which, in the open position of the valve, access to the coking drum is performed. In addition, the valve housing comprises a guide tube which is screwed in operation on the coking drum. In the open position, the tube bridge is aligned with the guide tube. In the closed position, the guide tube is closed by the closed part of the lid in one piece. The sealing in the closed position is obtained by a combination of a dynamic sealing seat with a static sealing seat. The dynamic sealing seat is obtained by a plurality of pistons disposed on the periphery of the guide tube, which pistons press with a wedge against a corresponding corner surface of a sealing ring. By an axial movement of the piston, the sealing ring is moved downwards and presses against the seal. The piston is elastically prestressed so that it can compensate for thermal expansions. By the dynamic sealing system, the sealing force is applied to the seal via the seal ring. [0009] The known system is relatively complex and can only produce limited sealing forces. As a result, for the valve with only one known seal, the manufacturing and maintenance costs are relatively high. In addition, the safety of the single-gate valve is not high enough. The object of the invention is to improve a valve with a single cap and a closure device of the type indicated at the beginning, with regard to their safety of operation. The object of the invention is achieved with a closure device for industrial valves of industrial installations, in particular chemical and petrochemical installations, with a cover for sealing an opening for a flow of fluid and with a sealing seat. The lid is disposed between the sealing seat and a support device 5 for applying to the lid a bearing force and the lid is able to be pressed by the support device against the sealing seat . The support device comprises, in a casing, a plurality of pistons and a transmission element for transmitting the bearing force to the cap, which is arranged between the pistons and the cap and extends along the circumference. of the operculum. The pistons are connected to each other in fluid communication by a supply line for a hydraulic fluid. An essential difference with respect to the known closure device consists in the fact that, in the invention, the lid is pressed against the sealing seat. In the state of the art, conversely, the sealing seat is pressed against the cover. By the invention, the sealing and thus the operational safety of the system are improved since large bearing forces can be applied. The design and control are significantly simplified, since the pistons are in fluid communication through the supply line, so that all pistons can be operated with the same pressure. In other words, the pistons are connected in series. The individual control and thus the adaptation of the individual forces of the pistons, as practiced in the state of the art for the implementation of the dynamic sealing seats, is omitted. This brings the advantage that the operation is simplified. To open the closing device, the pistons are controlled off load. This is done centrally since the pistons are in fluid communication. In the closed position of the seal, the pistons are subjected to a pressure, so that the necessary support force is generated which presses the seal against the seal seat. An adaptation of the pressure during operation, if necessary, is possible by the control of the hydraulic pressure. The invention applies to valves with a single seal and to other closure devices for industrial installations, which interrupt a flow of fluid by means of a plate or cap and which comprise a sealing seat. According to a preferred embodiment of the closure device of the invention, the transmission element comprises a ring, a first end face is adjacent to the cap and a second end face is attached to the pistons.
    [0003] The ring implements a distribution of forces applied by the pistons, around the periphery of the cap, which results in a homogeneous support force.  According to another additional feature of the invention, the lifting direction of the pistons may be perpendicular to the cap.  Thus, it is not necessary to redirect the forces, which makes possible a simple and compact design.  According to yet another additional feature of the invention, pushers may be arranged between the pistons and the transmission element, in particular the ring, each of the pushers connecting the piston corresponding to the transmission element.  This has the advantage that, on the one hand, the piston is spaced from the transmission element 10 and that, on the other hand, the introduction of the bearing force into the transmission element by the pusher, can be optimized.  According to yet another additional feature of the invention, the transmission element, in particular the ring, may be subjected to a spring force which acts perpendicularly to the lid.  The spring force preferably acts in the direction of the seal.  By this, the lid is prestressed against the sealing seat, so that, during a translational movement of the lid, when there is no support force by the pistons, an effect sufficient sealing is maintained.  Advantageously, the pusher is connected to a spring, the spring being in abutment against a pusher guide ring which is attached to the housing.  According to yet another additional characteristic of the invention, the pistons are arranged in a piston guiding ring in which the supply duct for the hydraulic fluid is formed.  The piston guide ring provides compact layout and robust piston support and is easy to mount.  [0020] According to yet another additional characteristic of the invention, the piston guide ring may comprise pressure chambers which are arranged below the piston bottoms and which are in fluid communication via the supply duct. .  In the operating state, the pressure chambers are filled with a hydraulic fluid, so that a rapid control, in case of actuation, is made possible.  Advantageously, the piston guide ring comprises an annular cover which closes the lower face of the piston guide ring.  By this, the maintenance of the pistons and the supply duct is made easier.  [0022] The object of the invention is also achieved with a gate valve, in particular a single-gate valve, for chemical and petrochemical installations, with a casing, in particular a valve casing.  The housing comprises a closable guide tube and a cover which is adapted to be moved to an open position and to a closed position and vice versa, a sealing seat being associated with the guide tube, which seat extends along the periphery of the guide tube and, in operation at least in the closed position, sealing against the lid from above.  The lid is disposed in a support plate movable in translation and is movable relative to the support plate in the direction of the longitudinal axis of the guide tube.  A support device is disposed in the housing below the seal to press the seal in the closed position against the seal seat.  The support device comprises a plurality of pistons and a transmission element, in particular a ring, for transmitting the bearing force on the cover.  The pistons are connected to each other in fluid communication by a supply line for a hydraulic fluid.  The transmission element is disposed between the pistons and the seal and extends along the periphery of the seal.  The gate valve according to the invention has various advantages.  The invention allows to generate higher support forces.  In addition, the support device is disposed below the cover where more space is available, so that the various components of the support device can be made to larger dimensions.  An essential difference from known single seal valves is that, in the invention, the entire seal is squeezed against the seal seat.  In the state of the art, conversely, the sealing seat is pressed against the cover.  According to the invention, it is provided that the cover is disposed in the support plate and that it is movable relative to the support plate in the direction of the longitudinal axis of the guide tube.  The support plate and the cap 30 then form two independent components that are movable relative to each other.  In contrast to this, the seal of the state of the art is formed in one piece, so that it can not be pressed, as a whole unit, against the sealing seat 3025277 6 since the one-piece seal is mounted in the valve housing, movable in translation in its entirety.  In addition, the support function of the single-seal valve according to the invention can be used to lock the lid in the closed position, so that an inadvertent displacement of the lid may be prevented in a safe way.  This is not possible with a traditional dynamic sealing seat.  The mobile cover relative to the support plate has the additional advantage that it can be removed from the support plate and that it can be replaced for maintenance purposes.  The support plate remains in the housing.  The separation of the lid and support plate functions has the additional advantage that the lid and the support plate are decoupled from one another, so that a thermal deformation of the operculum has no or only little influence on the support plate and thus on the guiding of the lid in the support plate.  The separate seal further has the advantage that different materials can be used for the seal and the support plate.  The quality of the seal material may be adapted to the particular requirements that the seal, as the closure member of the coker drum, must meet.  This is also valid for the extra-fine surface treatment which can be limited to the cover.  By this, the manufacturing costs are reduced.  Regarding the advantages of the invention provided by the pistons in fluid communication by the supply conduit, in particular by the common supply conduit, reference is made to the explanations given in relation to the closure device according to the invention, these explanations being valid also in relation to the single-gate valve.  According to a further feature of the invention, the cap may be disposed in the support plate with a radial clearance.  By this, it is effectively avoided that thermal expansions of the cap are transmitted on the support plate.  In addition, the insertion of the seal into the support plate during assembly and maintenance work is made easier by the radial clearance.  Preferably, the shape of the cap is adapted to the cross section of the guide tube.  In general, the guide tube has a circular cross section.  In this case, the seal forms in particular a circular disk.  The circular disk has the advantage that the thermal deformation is radial.  On non-circular plates or covers, as in the state of the art, the thermic deformation is done in an uncontrolled manner, which can cause problems concerning the sealing and guiding of the lid.  According to a preferred embodiment, the support plate comprises a passage opening and a receiving opening, the lid being disposed in the receiving opening.  In the open position, the passage opening is aligned with the guide tube.  The passage opening may also be designated as a tube bridge.  In the closed position, the seal located in the passage opening seals the guide tube.  [0033] The receiving aperture may include a conically enlarging edge downwardly.  By this, it is obtained that any impurities that would happen to be between the edge of the lid and the edge of the receiving opening, can be discharged down.  [0034] Direction indications "up" and "down" refer to the mounting position of the valve.  In the mounting position of the valve, the longitudinal axis of the guide tube 20 is oriented vertically.  The support plate with the cover is moved in the horizontal direction, that is to say perpendicularly to the longitudinal axis of the guide tube.  In the mounting position, the closure device is located below the lid.  In the closed position, the lid is located between the closure device and the coking drum.  According to another additional characteristic of the invention, the support plate is disposed between an upper guide plate and a lower guide plate which each comprise, close to the guide tube, a passage opening, the medium being encapsulated between the guide plates.  With these two guide plates, a linear guide of the support plate is obtained.  In addition, the guide plates seal the support plate and thus the seal, so that neither in the open position nor in the closed position, gases or liquids can penetrate into the valve housing.  The sealing of the valve housing can be further improved by applying an overpressure to the valve housing.  The guide tube may form an upper and lower manifold, where the upper manifold, together with the upper seal seat, may be removed from the valve housing to form a maintenance opening through which the lid can be removed from the housing.  With the maintenance opening, the opening which is anyway provided in the valve housing near the guide tube, is enlarged and that so that the seal can be removed by the maintenance opening.  It is therefore no longer necessary to remove the lid of the housing in the longitudinal direction which represents work of a certain size.  To replace the cap, it is sufficient to remove the guide tube together with the upper seal seat so that, then, the cap can be removed from the housing from the top.  The upper sealing seat comprises a static sealing system which acts at least in a simple manner and which cooperates with an upper face of the lid.  As opposed to the state of the art, it is therefore not necessary to provide a dynamic sealing system that generates the necessary sealing force.  Instead, a relatively simple design seal system against which the entire seal is pressed can be used instead.  It is also possible, to improve the sealing function, to use a static sealing system acting in a double, triple or quadruple manner.  When using a double acting sealing system, two individual sealing means are combined with each other.  And for a triple acting sealing system, three individual sealing means are combined with each other and so on.  According to a particularly preferred embodiment, a sealing seat having a sealing system acting in a triple manner may comprise at least one sealing edge and scraper arranged radially inside, at least one seal 25. metallic seal arranged radially on the outside and, in between, a gas barrier, especially a vapor barrier.  The radially inward sealing and scraping edge, also referred to as the "scraper", forms a metallic seal which seals with respect to the surface of the seal.  In addition, impurities that are fixed on the surface are scraped with said edge.  With regard to the radially outwardly arranged seal, it is also a metal seal that seals with respect to the seal surface.  With the gas barrier, the penetration of gases and liquids into the valve housing is effectively prevented.  Preferably, the support device is disposed along the periphery of the lid.  By this, we obtain that the opening formed by the guide tube is free of construction elements, so that petroleum coke or other residues can be removed from the coking drum without difficulty by the guide tube to outside.  The arrangement of the support device along the periphery of the seal means that the support device does not exceed the inner diameter of the guide tube.  Preferably, the support device comprises a ring which, in the closed position, is adjacent to the underside of the cover and which can be subjected to a bearing force acting in the direction of the axis. longitudinal guide tube.  By this, a homogeneous bearing force is obtained which is transmitted from the support device to the cover, so that a homogeneous sealing effect is obtained on the entire periphery of the cover.  The bearing force acting in the direction of the longitudinal axis of the guide tube therefore acts, in mounting position, in the vertical direction, that is to say perpendicularly to the lid.  [0041] Preferably, the ring forms a lower sealing seat, particularly in the form of an additional metallic seal which makes tight with respect to the underside of the lid.  The ring thus has the dual function of, on the one hand, transmitting the sealing force of the support device to the seal and, at the same time, forming a seal which prevents impurities from entering the seal. inside the valve housing 20.  According to the invention, the support device comprises a plurality of force means, in the form of pistons, arranged and distributed around the periphery of the cover which each generates a force acting in the direction of the longitudinal axis of the guide tube for subjecting the lid to a supporting force.  By this, it is obtained that the pressing force is introduced into the lid at several places around the perimeter of the lid, so that the lid is pressed homogeneously against the upper sealing seat.  The support device, in particular the ring, may be prestressed with respect to the projection.  By this, we obtain that the ring press against the cap with a continuous force, so that the sealing function, including the ring, is maintained even when the support device does not actively operate.  [0044] Preferably, a plurality of spring assemblies, in particular flat spring assemblies, are arranged and distributed around the periphery of the ring which subject the ring to a spring force each acting in the direction of the axis. longitudinal guide tube.  By this, the sealing force of the lower sealing seat is generated, even when the support device is in a state of rest.  The invention will be better understood, and other objects, features, details and advantages thereof will appear more clearly in the explanatory description which follows, with reference to the appended drawings given solely by way of illustrative example. Several embodiments of the invention and in which: FIG. 1 is a perspective view of a single-gate valve; FIG. 2 is a longitudinal section of the single-gate valve of FIG. FIG. 3 is an exploded view of the single-gate valve of FIG. 1; FIG. 4 is a detailed view of the upper sealing seat; FIG. 5 is a sectional view of the hydraulic support device of FIG. a closure device according to one embodiment of the invention which can be mounted, for example, in the single-gate valve of FIG. 1; FIG. 6 a perspective view of the support device of the invention; FIG. 5; FIG. 7 the view in per FIG. 8 is a perspective view of FIG. 6 without a piston guide ring; FIG. 9 is a perspective view in partial section of a valve with a single cover.  The valve with a single seal according to Figure 1 is used in coking plants, particularly in delayed coking plants, called "Delayed Coker" facilities, where coker drums are provided with closure devices.  Concretely, the single-gate valve shown in FIG. 1 is used to close the bottom outlet opening of a coking drum ("Bottom Deheading").  It is also possible to use the design according to the invention in a closure member used to open and close the upper outlet opening of the coking drum ("Top De-heading").  In addition, the design according to the invention, more generally the invention, can be used in the context of closure devices operating in other fields of industry such as ethylene, FCCU, phosgene etc.  In general, a closure device according to the invention can be used as closure member in chemical and petrochemical plants or in other industrial installations where hot and / or reactive fluid flows are handled.  In the context of the present invention are disclosed and claimed individually, the gate valve as the upper unit, on the one hand, and the closure device 10 with cap, sealing seat and support device as part of the gate valve, on the other hand.  The closure device is not limited to use in a gate valve, in particular in a single gate valve, but it can also be used in other industrial valves in industrial installations where fluid flows are regulated. .  With the aid of the single-gate valve shown in FIGS. 1 to 3, the generally used design features will be explained.  However, instead of the manually operated support device of the single-gate valve shown in FIGS. 1 to 4, a hydraulic support device is used in the context of the present invention, this device being explained with reference to FIGS. Figures 5 to 8 by way of example.  The general design features described below are maintained in the embodiment according to the invention.  The single-gate valve shown in Figure 1 comprises a valve housing 10.  The valve housing 10 is disposed between two covers 27 which extend in the longitudinal direction of the valve housing 10.  The two covers 27 and the valve housing 10 are screwed to each other.  The two covers enclose the displacement races of the elements arranged in the valve housing, which are necessary to actuate the valve with a single seal.  The valve housing 10 comprises a guide tube 11 which constitutes a passage 28 for a fluid.  The fluid passage 28 is aligned, in the mounting state, with the outlet opening of the coker drum.  (not shown)  Through the fluid passage 28, the petroleum coke portions which are in the coking drum are removed, for example by waterjet cutting.  The guide tube 11 comprises an upper pipe 18 shown in FIG. 1, which is screwed on the valve housing 10.  To the guide tube 11, and concretely to the upper pipe 18, is associated a sealing seat 13a which is visible in FIG. 2.  The upper pipe 18 comprises an annular flange 29 which is screwed on the valve housing 10.  In FIG. 1, it may also be noted that the inside diameter of the guide tube 11 comprises a hard shield 30 which protects the guide tube 11 from abrasive wear.  The guide tube 11 extends along a longitudinal axis drawn in Figure 1.  In the mounting state, the longitudinal axis extends in the vertical direction.  The longitudinal axis of the guide tube is aligned with the longitudinal axis of the coking drum (not shown).  In FIG. 1, it may also be noted that the valve housing comprises a connection 31 for a flushing gas or a barrier or stop gas, which connection is arranged at the upper edge of the valve housing.  The flushing gas and barrier gas connection supplies the sealing seat 13a with a flushing gas or a barrier gas.  Specifically, is used in the valve to a single seal according to Figure 1 of the steam as a barrier gas.  At the lower longitudinal edge of the valve housing 10, a support device 26 is provided.  The mechanical jack 32 shown is replaced by the hydraulic support device according to FIGS. 6 to 9.  The other design features described above are maintained.  On the two covers 27, additional gas connections 45 are provided which serve to apply a sealing pressure to the two covers or to the valve housing.  From the cover 27 which is located on the right in FIG. 1, an actuating bar protrudes with the aid of which the valve with a single cap can be placed in the open position and in the closed position.  In operation, the actuating bar is connected to a suitable drive.  [0057] In FIGS. 2 and 3, the design of the single-gate valve according to FIG. 1 is recognized.  In the valve housing 10, a cap 12 is disposed which is able to be moved to an open position and to a closed position and vice versa.  In other words, the seal may be alternately in the open position and the closed position depending on whether the outlet opening of the coker drum is to be opened or closed.  In the open position, the cover 12 releases the guide tube 11, so that the coking drum connected to the guide tube becomes accessible.  In the closed position, the seal 12 closes the guide tube and prevents gases, liquids and particles from escaping.  The sealing of the lid 12 is obtained by a sealing seat 13a.  The position indications "up" and "down" refer to the operating position of the valve with a single cap which is arranged horizontally.  As can be seen in Figs. 2, 3 together with Fig. 1, the sealing seat 13a extends along the periphery of the guide tube 11, concretely along the periphery of the upper manifold.  A particularity of the single-gate valve according to FIGS. 1 to 3 consists in the fact that the cover 12 is arranged in a support plate 14.  The seal 12 and the support plate 14 are two distinct elements which have different functions.  The cover 12 serves only to seal the guide tube 11.  The support plate 14 supports the cover 12 and moves it to the open position or to the closed position or vice versa.  For this, the support plate 14 comprises a receiving opening 16 in which is disposed the lid 12 (see Figures 2, 3).  The dimensions of the receiving aperture 16 are chosen such that the cover 12 is movable in the direction of the longitudinal axis of the guide tube 11 relative to the support plate 14.  In other words, the cover 12 can be moved perpendicular to its radial extent.  For this purpose, a suitable clearance between the cover 12 and the receiving opening 16 is adjusted which is chosen such that a warpage of the two elements by thermal extension 20 of the cover 12 and the support plate 14 is avoided .  The purpose of the axial mobility of the seal 12 is to make possible a support of the seal 12 against the upper static sealing seat 13a.  The bearing force is obtained by the support device 26 already mentioned which is arranged, in the mounting position, below the cover 12.  With the axially movable lid 12 and the support device 26, it is obtained that the lid can be pressed, in the closed position thereof, against the upper static sealing seat 13a, if although the sealing force between the upper seal seat 13a and the seal 12 is increased.  The support plate 14 comprises, apart from the reception opening 16, a passage opening 15 which can also be designated as a tube bridge.  In the open position, the passage opening 15 is aligned with the fluid passage 28 of the guide tube 11 and releases the coking drum.  The diameter of the passage opening 15 or the pipe bridge is chosen such that the upper sealing seat 13a and the lower sealing seat 13b described elsewhere make the passage opening 15 tight. it is avoided that gas and liquids enter the valve housing 10.  The receiving opening 16 and the opening 15 are juxtaposed in such a way that they each enter the guide tube 11 by a translatory movement of the support plate 14, in order to respectively carry out the position of opening and closing position of the valve to a single seal.  The support plate 14 is disposed between two guide plates 17 which encapsulate the support plate 14.  The two guide plates 17 and the support plate 14 are arranged parallel in plan.  For actuation of the support plate 14 and thus of the cover 12 disposed in the support plate 14, an actuating bar 34 is provided which is attached in shape connection to one end of the support plate 14 so that pushing and pulling forces can be transmitted to the support plate 14.  The actuating bar 34 protrudes from one of the covers 27 and can be connected to a drive not shown.  The actuator bar 34 is disposed between the two guide plates 17 which are spaced parallel to each other.  In Figure 3, it is also visible that the upper pipe 18 can be removed from the valve housing 10 entirely.  That is, the upper portion of the guide tube 11, including the seal seat 13a, can be removed completely, whereby a maintenance opening is formed in the valve housing 10 which is sufficiently large to make possible a removal of the seal 12.  For this purpose, the upper tubing 18 is formed as a unit to be handled as a whole.  The upper tubing 18 comprises a support ring 35 which is mounted on the annular flange 29.  The support ring 35 and the annular flange 29 are concentric.  The inner face of the support ring 35 and the upper end face of the support ring 35 are provided with the hard shield 30.  On the lower face of the support ring 35 is disposed the upper sealing seat 13a which is arranged concentrically with respect to the support ring 35 and, in general, with respect to the upper manifold 18.  The upper sealing seat 13a is screwed onto the support ring 35.  The upper sealing seat 13a and the other upper tubing components, including the support ring 35 and the annular flange 29, form a unit to be handled as an entire unit which is removably attached to the housing. valve 10 and which can be removed from the valve housing 10 as a unit.  In the mounting state according to FIG. 2, it is visible that the tubing 18 is disposed in a casing receiving 36 of the valve casing 10.  The casing receiving 36 is also clearly visible in FIG. 3 and is formed in one piece with the valve casing 10.  The casing receiving 36 forms a retaining ring into which the upper tubing 18 is inserted, as can be seen in FIG.  The housing receiving 36 is drawn in FIG. 2 together with the remainder of the wall of the valve housing 10 as a transparent component.  Figures 2 and 3, it is also visible that the guide tube 11 comprises a lower pipe 19 which is screwed on the housing below the lid 12.  For removal of the seal 12 for maintenance purposes, this includes a central tapping 37 into which a hook may be inserted, for example.  The lid 12 forms a circular disk.  In this sense, the shape of the cover 12 corresponds to the cross section of the guide tube 11.  The shape of the receiving opening 16 is correspondingly circular.  [0068] The sealing function of the single-gate valve according to FIG. 1 is explained with reference to FIG. 4.  The upper sealing seat 13a comprises three sealing components which lead to a sealing system acting in a triple manner.  Sealing systems acting in a simple or multiple manner may be used.  The upper sealing seat 13a is a static sealing seat.  By this means a sealing seat which serves as a stop for the cover 12 when it is subjected to a bearing force against the upper sealing seat 13a.  In other words, the upper sealing seat 13a can not escape when the cover 12 is pressed against it.  Contrary to this, dynamic sealing seat comprises a sealing seat 25 which actively applies the necessary support force to the seal 12.  Compared to such known dynamic sealing seats, the upper sealing seat 13a is static.  The support force necessary for the sealing effect is applied by the axially movable cover 12.  The upper sealing seat 13a comprises a sealing and scraping edge 20, also referred to as a "scraper", disposed radially on the inside.  The sealing and scraping edge 20 forms the inner edge of the upper tubular 3025277 16 18, which bears on the cover 12.  The sealing and scraping edge 20 forms a metallic seal which bears on the cover 12.  The other function of the sealing edge and scraping 20 is to scrape any impurities that would be glued to the cover 12.  Another seal of the upper seal seat 13a is formed by the metal seal 21 which is disposed radially outwardly with respect to the sealing and scraping edge 20.  The metal seal 21 forms the outer periphery of the upper sealing seat 13a and is prestressed against the cover 12 by a spring 38.  Other arrangements or possibilities of prestressing the metal seal 21 are conceivable.  The upper sealing seat 13a further comprises a compensator 39 which is arranged concentrically with respect to the upper pipe 18.  The compensator 39 is a corrugated tube and can be compared to a very strong spring.  The compensator 39 is disposed in an annular groove 40 which is formed above the metal seal 21 on the periphery of the upper tubing 18.  The annular groove 40 is delimited downwards by a receiving ring 41 in which the springs 38 are arranged for the metal seal 21 arranged radially on the outside.  The receiving ring 41 bears against the metal seal 21.  It is also possible to form the receiving ring 41 and the metal seal 21 in one piece.  The third sealing system of the upper sealing seat 13a is formed by a gas barrier, in particular a steam dam, 22 which is connected to the flushing gas and dam gas connection 31 described with reference to FIG. figure 1.  The steam barrier 22 is formed by another annular groove 42 which extends concentrically between the sealing and sealing edge 20 and the metal seal 21.  For the upper sealing seat 13a, there are also other possible embodiments.  In Figure 4 is also visible that the receiving opening 16 of the support plate 14 forms a flared concentrically downward edge which serves to evacuate down any impurities that would be placed between the operculum 12 and the receiving opening 16.  The seal 12 has a radial clearance in the receiving opening 16 in order to compensate for thermal deformation, on the one hand, and in order to make safe the axial movement of the seal with respect to the support plate 14, on the other hand.  For the abovementioned bearing force of the cover 12 against the upper sealing seat 13a, a support device 26 is provided which is arranged below the cover 12.  In other words, the cover 12 is disposed between the support device 26 and the upper sealing seat 13a which serves as an abutment for the support device 26.  The bearing force of the support device 26 is applied by several force means 23 arranged and distributed around the periphery of the cover 12.  It is disclosed and generally claimed with reference to the invention and in particular with reference to the embodiment according to Figure 4, that the force means 23 are disposed on the outer face of the cover 12 .  In other words, the force means 23 are arranged approximately at the same level as the outer edge of the cover 12.  By this, it is surely obtained that the force means 23, and in general the support device 26, are arranged outside the fluid passage 28.  In the single-gate valve according to FIGS. 1 to 5, in the closed position, the fluid passage is free of components with the exception of the seal 12.  The force means 23 arranged and distributed around the perimeter of the cover 12 each serve to apply the bearing force to the cap in the direction of the longitudinal axis of the guide tube.  In other words, the bearing force acts perpendicular to the seal 12.  The mechanical support device shown in FIG. 4 is replaced in the exemplary embodiment according to the invention by the hydraulic support device 26 according to FIGS. 5 to 8.  [0080] FIG. 5 shows a section of a closure device for industrial plant valves, which is used in the gate valve shown in FIGS. 1 to 4.  The closure device comprises a plate 12 and a sealing seat 13a (not shown).  The plate 12 serves to close an opening for a flow of fluid, for example the guide tube 11.  To this end, the plate 12 is movably disposed in a housing 10, in particular in the valve housing 10.  The plate 12 corresponds to the cover 12 shown in FIGS. 1 to 4.  The plate 12 is disposed between the sealing seat 13a and the hydraulic support device 26.  The support device 26 serves to apply to the plate 12 a bearing force which presses it against the sealing seat 13a.  the support device 26 comprises a plurality of pistons 48 which are arranged along the periphery at the edge of the plate 12.  In other words, the pistons 48 are arranged on a circular line.  The pistons are arranged equidistantly.  For the transmission of the piston force on the plate 12, a transmission element in the form of a ring 50 is provided.  The ring 50 is disposed between the pistons 48 and the plate 12 in an upwardly open groove in the casing 10.
    [0004] The ring 50 protrudes from the upper edge of the circular groove and is permanently supported on the underside of the plate due to spring preload. The ring 50 has a dual function. On the one hand, the ring 50 functions as a force transmission means for pressing the plate 12 against the upper seal seat 13a. On the other hand, the ring 50 itself performs a sealing function and forms the lower sealing seat 13b which makes the plate 12 sealed from below. In addition, the ring 50 blocks the gate valve or the closure device in the closed position and secures against any inadvertent opening, by the very large bearing forces that can be generated by the support device 26. The function Locking is not feasible with traditional dynamic sealing seats which are designed to only increase the sealing force. As can be seen in FIGS. 4 and 6, the ring 50 overlaps as well with the plate 12 as with the edge of the receiving opening 16 in the support plate 14. Between the lower edge of the the receiving opening 16 and the ring 50, a sufficient clearance is adjusted to make possible the axial movement of the ring 50 in the longitudinal direction of the guide tube or perpendicularly to the plate 12, by which movement the force of the support is applied to the plate 12. In other words, it is thus avoided that the ring 50 is blocked by the support plate 14. The plate 12, the ring 50 or the annular groove, and the pistons 48 are arranged concentrically. The pistons 48 are fluidly connected by a common supply line 49 for the supply of hydraulic fluid. Pistons 48 are thus connected to each other in series. The supply duct 49 is connected to a not shown hydraulic connection by which the pistons 48 can be controlled centrally. The hydraulic connection can be connected to a hydraulic pump that is not shown either. In operation, the supply duct 49 and the pressure chambers 58 which are still to be explained are completely filled with a hydraulic fluid. As can be seen in FIG. 5, the ring 50 comprises axial end faces 51, 52, the first end face 51, the upper face being directly resting on the plate 12. The second end face 52, the lower face of the ring 50 is connected to the pistons 48, so that the bearing force generated by each of the pistons 48 is transmitted via the ring 50 to the plate 12. The connection between the pistons 48 and the Ring 50 is formed by pushers 54 which are arranged between the pistons 48 and the ring 50. In other words, each piston 48 is associated with an individual pusher 54 which connects the corresponding piston 48 to the ring 50. The raising direction of the pistons 48 is perpendicular to the plate 12. In other words, the pistons 48 are driven parallel to the longitudinal axis of the guide tube 11. The longitudinal axis of the pushers 54 and the lifting direction of the pistons 48 are aligned. Each pusher 54 comprises an upper portion and a lower guide portion 62, 63 which are preferably aligned. The upper guide portion 62 is mounted axially movable in a bore in the housing 10. The bore opens into the bottom of the annular groove of the ring 50. The dimensions of the upper guide portion 62 are selected so that it can plunge into the annular groove and can apply a bearing force to the ring 50. [0090] The lower guiding portion 63 is housed in a guide ring of pushers 56. For this purpose, the The lower guide portion 63 passes through a bore formed in the pusher guide ring 56 and projects beyond the pusher guide ring 56 down to the piston 48 (see FIG. 8). The push guide ring 56 is disposed in a corresponding annular recess in the housing 10 and is attached to the housing 10, for example by a force link. Between the upper and lower guide portions 62, 63 is a shoulder 65 which protrudes from the guide lower portion 63 in the radial direction. The lower face of the shoulder 65 forms a bearing surface for a spring 55 which is disposed between the shoulder 65 and the pusher guide ring 56 and prestresses the pusher 54 against the ring 50. this, a permanent prestressing force is applied to the ring 50, which acts in the direction of the plate, so that when opening or closing the plate 12, the sealing effect is maintained. Other springs 5 than the flat springs shown in Fig. 5 are possible. The ring 50, the pushers 54 and the pistons 48 are sealed relative to the housing 10 by means of sealing elements 53, for example sealing ropes and annular seals made of a heat-resistant material. As can be seen in FIGS. 5 and 6, the piston 48 and the pusher 54 10 form individual components which bear against each other for the transmission of force. It is also possible to form pistons 48 and corresponding pushers 54 in one piece. The advantage of individual components is easier mounting. The other pistons 48 and pushers 54, which are not shown, are correspondingly formed. The number of pistons 48 depends on the nominal width of the plate 12. For a nominal width of 1800 mm for a FCC unit ("fluid catalyzed cracking", ie catalytic cracking unit on fluidized bed in French) approximately 20 pistons may be sufficient around the circumference. The pistons may each have a diameter of about 8 to 10 cm. Higher or lower nominal widths may necessitate a greater or smaller number of pistons, which is determined by those skilled in the art. The piston diameter can be adapted to the particular operating conditions during the design of the support device. The support of the pistons 48 is performed by a piston guide ring 57 which is connected to the housing 10, for example screwed on the latter. The threads are visible in FIG. 8. The piston guide ring 57 comprises a number of cylinder bores corresponding to the number of pistons. The cylinder bores are aligned with the longitudinal axis of the push rods 54. The piston guide ring 57 bears on the push guide ring 56 and fixes the latter in the recess in the housing 10. [0096 In the lower face 61 of the piston guiding ring 57 is formed the supply duct 49, for example in the form of a connecting groove, which connects in fluid communication all the pistons 48 (see FIG. Figures 5, 7). The supply duct 49 thus forms a pressure channel which is delimited, on the one hand, by the piston guide ring 57 and, on the other hand, by an annular cover 60 which is connected , for example screwed, to the lower face 61 of the piston guide ring 57. Between the cover 60 and the lower face 61 of the piston guide ring 57 is inserted a sealing member 53. The cover 60 the piston guide ring 57 and the push guide ring 56 are arranged concentrically. The piston guide ring 57 forms a number of pressure chambers 58 corresponding to the number of pistons 48, which chambers are aligned with the cylinder bores of the pistons 48. The diameter of a pressure chamber 58 corresponds to diameter of the respective cylinder bore. The supply duct 49 connects the pressure chambers 58 and thus establishes the fluid connection between the pistons 48. The pressure chambers 58 are separated from the corresponding cylinder bore by a stop 66 which holds the piston in the state without pressure and which prevents the mouth of the supply duct 49 is blocked when the hydraulic pressure drops too strongly (Figures 5 to 7). [0099] In FIG. 9, another embodiment of the invention of a single-gate valve is shown, which is distinguished from the single-gate valve according to FIG. 1 by the additional drive 47. It is clearly visible in FIG. 9 that the support plate 14 receives, on the one hand, the passage aperture 15 and, on the other hand, the cap 12 as an individual component. The cover 12 is formed as a circular disk 20 which is arranged, in the closed position, concentrically with the guide tube 11.
    权利要求:
    Claims (15)
    [0001]
    REVENDICATIONS1. Closing device for industrial valves of industrial installations, particularly chemical and petrochemical plants, with a plate or cover (12) for closing an opening for a flow of fluid and with a sealing seat (13a), characterized in that the cover (12) is arranged between the sealing seat and a support device (26) for applying to the cover (12) a bearing force and in that the cover is suitable for being pressed by the support device (26) against the sealing seat (13a), the support device (26) comprising, in a housing (10), a plurality of pistons (48) and a transmission member for the transmission of the bearing force to the seal (12), which is arranged between the pistons (48) and the seal (12) and extends along the periphery of the seal, and the pistons (48) being connected to each other in fluid communication by a supply line (49) for a hydraulic fluid.
    [0002]
    2. Closure device according to claim 1, characterized in that the transmission element comprises a ring (50) of which a first end face (51) is adjacent to the cap (12) and a second end face (52). ) is attached to the pistons (48).
    [0003]
    3. Closure device according to claim 2, characterized in that the lifting direction of the pistons (48) is perpendicular to the lid (12).
    [0004]
    4. Closure device according to any one of the preceding claims, characterized in that pushers (54) are arranged between the pistons (48) and the transmission element, in particular the ring (50), each of the pushers connecting the corresponding piston (48) to the transmission element.
    [0005]
    5. Closure device according to any one of the preceding claims, characterized in that the transmission element, in particular the ring (50), is subjected to a spring force which acts perpendicularly to the cover (12).
    [0006]
    6. Closure device according to claim 4 or 5, characterized in that the pusher (54) is connected to a spring (55), the spring (55) being in abutment against a pusher guide ring (56) which is attached to the housing (10).
    [0007]
    Closure device according to one of the preceding claims, characterized in that the pistons (48) are arranged in a piston guiding ring (57) in which the supply duct (49) for the hydraulic fluid is form.
    [0008]
    Closing device according to Claim 7, characterized in that the piston guide ring (57) comprises pressure chambers (58) which are arranged below the piston bottoms (59) and which are in communication with each other. of fluid through the supply line (49).
    [0009]
    Closure device according to claim 7 or 8, characterized in that the piston guide ring (57) comprises an annular cover (60) which closes the lower face (61) of the piston guide ring ( 57). 10
    [0010]
    10. A gate valve for chemical and petrochemical installations, with a housing (10) which comprises a closable guide tube (11) and a cover (12) which is able to be moved to an open position and to a position closing and vice versa, a sealing seat (13a) being associated with the guide tube (11), which seat extends along the periphery of the guide tube (11) and, in operation at least in the position of 15 closing, sealing from above against the cover (12), characterized in that the cover (12) is arranged in a support plate (14) movable in translation and is movable relative to the support plate ( 14) in the direction of the longitudinal axis of the guide tube (11), a support device (26) being arranged in the housing (10) below the cover (12) in order to press the cover ( 12) in the closed position against the sealing seat (13a), the support device (26) comprising a plurality of pistons (48) and a transmission element, in particular a ring (50), for the transmission of the pressing force on the cover (12), the pistons (48) being connected to each other in fluid communication via a conduit of fed (49) for a hydraulic fluid and the transmission member being disposed between the pistons (48) and the seal (12) and extending along the periphery of the seal.
    [0011]
    11. A gate valve according to claim 10, characterized in that the seal (12) is disposed in the support plate (14) with a radial clearance.
    [0012]
    12. A gate valve according to claim 10 or 11, characterized in that the shape of the cap (12) is adapted to the cross section of the guide tube (11) and forms in particular a circular disk. 3025277 24
    [0013]
    A gate valve according to any one of claims 10 to 12, characterized in that the support plate (14) has a passage opening (15) and a receiving opening (16), the seal (12) being disposed in the receiving opening (16). 5
    [0014]
    14. A gate valve according to claim 13, characterized in that the receiving opening (16) comprises an edge enlarging conically downwardly.
    [0015]
    Gate valve according to one of Claims 10 to 14, characterized in that the support plate (14) is arranged between an upper guide plate and a lower guide plate (17), each of which is close to the a guide tube (11), a passage opening (15), the support plate (14) being encapsulated between the guide plates (17).
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    同族专利:
    公开号 | 公开日
    DE102014112220A1|2016-03-03|
    US20160061335A1|2016-03-03|
    US9784373B2|2017-10-10|
    ITUB20153240A1|2017-02-26|
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    法律状态:
    2017-05-26| ST| Notification of lapse|Effective date: 20170428 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102014112220.8A|DE102014112220A1|2014-08-26|2014-08-26|Shut-off device and gate valve with a shut-off device|
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