CA2165687C - Parallel slide gate valve - Google Patents
Parallel slide gate valveInfo
- Publication number
- CA2165687C CA2165687C CA002165687A CA2165687A CA2165687C CA 2165687 C CA2165687 C CA 2165687C CA 002165687 A CA002165687 A CA 002165687A CA 2165687 A CA2165687 A CA 2165687A CA 2165687 C CA2165687 C CA 2165687C
- Authority
- CA
- Canada
- Prior art keywords
- closure plates
- seal
- gate valve
- pressure medium
- slide gate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
- F16K3/16—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together
- F16K3/18—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members
- F16K3/188—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members by means of hydraulic forces
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
- F16K3/16—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together
- F16K3/18—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding Valves (AREA)
- Fluid-Driven Valves (AREA)
- Thyristors (AREA)
- Polarising Elements (AREA)
- Magnetic Resonance Imaging Apparatus (AREA)
- Multiple-Way Valves (AREA)
Abstract
Parallel slide gate valve with a casing (13) having an inlet nozzle and an outlet nozzle (16, 18), and in which is located a slide (21) containing two closure plates (1, 2), said slide being movable transversely to the nozzles (16, 18) located on a common axis (24) between two oppositely-lying seat surfaces (14, 15), the two closure plates (1, 2) or their seat surfaces (25, 26), in the closed position of the slide (21), being in sealing contact, under the action of a pressure medium introducible between the two closure plates or seal surfaces, with the respectively associated seat surface (14, 15) of the casing (13).
In the central area of the sides facing one another of the two closure plates (1, 2), reinforcing members (36....) operate.
In the central area of the sides facing one another of the two closure plates (1, 2), reinforcing members (36....) operate.
Description
2is~ss7 PARALLEL SLIDE GATE VALVE
The invention relates to a parallel slide gate valve with a casing having an inlet nozzle and an outlet nozzle, and in which there is located a slide containing two closure plates, said slide being movable transversely to the nozzles which are located on a common axis, between two oppositely-lying seat surfaces, both closure plates or their seal surfaces, in the closed position, being in sealing contact with the respectively associated seat surface under the action of a pressure medium introducible between the two closure plates or seal surfaces.
Such a parallel slide gate valve is generally known, particularly in the form of a so-called guide tube shutter. In this respect, reference is made to EP 0 326 787 B1, and to DE 40 11 274 C.
The object of the known constructions is that the parallel slide gate valve, while maintaining a good sealing function in its closed position, is subject during the opening and closing movement of the slide to only limited frictional forces on the seat and seal surfaces. This purpose is only partly fulfilled in the guide tube shutter according to DE 40 11 274 C, i.e.
only in the region of the guide tube. The spreading 2 2~ 6568' movement of the closure plates is effected purely mechanically, i.e. using the so-called 'wedge-in-wedge' principle. The problem arises here that, upon opening the fitting, specific return movement of the two closure plates is effected by means of separate plate spring assemblies. Accordingly, an uncontrolled adhesive friction arises between the seal surfaces of the closure plates on the one hand and the casing seal seats and the so-called guide plates on the other hand, resulting in a correspondingly high abrasive stress on the seal surfaces. Moreover, plate spring assemblies integrated in the actuating rod are necessary, in order to control the °wedge-in-wedge~~ mechanism.
The construction according to EP 0 326 787 B1 is extremely expensive and in addition'extremely heavy in construction. The closure plates fill practically the entire slot between the casing seal seats.
The purpose underlying the present invention is to provide a parallel slide gate valve of the type already mentioned, which is characterised on the one hand by a highly efficient sealing effect and on the other hand by minimum friction upon movement of the slide in the open position and vice versa, and by an extremely lightweight construction, and which adapts simply to deformations in the casing and thus in the seal seats.
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This purpose is fulfilled according to the invention by the characterising features of Patent claim 1.
Due to the claimed stiffening of the slide, relatively thin-walled closure plates may be used, which in an extreme case deform axially under the action of a pressure medium, with a corresponding contact on the casing seal seat in the closed position of the slide.
In this lightweight construction it is also possible to reduce the sealing force by reducing the pressure of the pressure medium in such a way that the slide may be operated, even at larger dimensions, with relatively low propulsive force. The thin-walled construction finally permits adaptation~of the slide to deformations of the casing or casing seal seats. Unacceptable deformation, particularly recessing in the closed position of the slide, is prevented by means of the stiffening members which are effective in the central area of the closure plates.
According to claim 2, there may serve as stiffening members either spacer webs located between the closure plates, or a stiffening ring, located between the closure plates, and extending radially within the surrounding seal surfaces of the two closure plates.
The same applies also with regard to the position of the mentioned spacer webs. These stiffening members simultaneously limit the maximum approach of the two closure plates upon opening of the fitting. For functional reasons they are also located only on the inner side of one of the two closure plates, in particular by welding.
Alternatively, stiffening of the closure plates in the central area may be effected by stiffening plates, preferably circular in shape, located on the sides facing one another.
Finally, it is also feasible in accordance with claim 2 to provide a stiffening ring, which is securely cannected, particularly welded, to both closure plates, so that there is formed on the one hand an annular space associated with the seal surfaces, and on the other hand a space formed within the stiffening ring, which is not in fluid connection with the other annular space. Only the outer annular space, which is associated with the seal surfaces of the two closure plates, communicates with a source of pressure medium and thus may be loaded by pressure medium with a consequent axial deformation, i.e. bulging of the seal surfaces in the closed position of the slide, so that the seal surfaces may be pressed against the seat surfaces of the casing.
In the variants with central stiffening plates or with stiffening members attached only on the inner side of a Closure plate, the two closure plates are, in all, movable relative to one another in an axial direction 2i6~fi8'~
under the action of a pressure medium, the space between the two closure plates being restricted in a fluid-tight manner from the environment by compensators extending along the outer circumference. Such a compensator is preferably formed by a pipe section, produced from a strip of metal bent in a corrugated manner, with at least one half-shaft extending over the circumference, said pipe section being welded fluid-tight along both its peripheral edges to the two closure plates, a pressure medium pipe opening through the corrugated pipe section into the space between the two closure plates.
The construction according to the invention is particularly suitable also for a parallel slide gate valve which additionally comprises a so-called guide tube (= guide tube shutter, or also named pipe bridge valve), which has two seal rings which, in the open position of the slide, may be pressed under the action of pressure medium against the seal seats of the slide casing, the pressure medium space associated with the seal rings of the guide tube being connected in fluid terms with the pressure medium space associated with the seal surfaces of the two closure plates. Thus one and the same pressure medium, or the same pressure medium unit, may be used both for pressing the seal rings of the guide tube and pressing the seal surfaces of the two closure plates.
A simple construction of the last-named embodiment is characterised in that the two closure plates of the slide and the two seal rings of the guide tube are respectively integrally connected together, i.e. form integral plate portions, the space between the two plate portions being closed fluid-tight from the environment at the edges, particularly by means of a compensator of the abovementioned type. The closure plates and seal rings then form part of a fluid-tight closed box, whose variable height is determined by the compensators mentioned. The corners of the said box are rounded in accordance with the contour of the seal surfaces of the closure plates or seal rings of the guide tubes. In this way minimum pressures are obtained on the closure plates and seal rings of the guide tube itself as well as in the transitional area between closure plates and seal rings when the latter are pressed against the casing seal seats.
In order to ensure a sufficient seal effect of the fluid medium duct in the closed position of the slide even upon failure of the pressure medium unit for the axial spreading of the closure plates, the pressure medium space between the seal surfaces of the closure plates in the closed position of the slide may be connected with the pressure side of the casing or its flow passage, so that the said pressure medium space is under system pressure. This is a safety feature not to be underestimated; only the gaseous components of the ' 21~~687 operating medium being used of course for this purpose.
During actuation, the internal pressure in the fluid-tight closed box is reduced, in order to obtain easy-running displacement of the shut-off member with or without guide tubes. Should unforeseen leaks occur, by means of introduction of rinsing medium, particularly rinsing vapour into the slide casing, the penetration of operating medium into the slide casing, contaminating the fitting within the casing, is avoided.
Claims 12 to 21 relate to a special seal arrangement for slide and guide tube, which is recommended for parallel slide gate valves of the type in question here especially when high pressures and temperatures are to be controlled.
Embodiments of the parallel slide gate valve according to the invention will be explained in more detail in the following with reference to the annexed drawings, which show:
Figure 1: a cross-section through a first embodiment of a parallel slide gate valve with guide tube;
Figure 2: a view, partially in side elevation, partially in longitudinal section, of the embodiment according to Figure 1;
Figure 3: a cross-section through a second embodiment of a slide with guide tube;
Figure 4: a longitudinal section through the embodiment according to Figure 3;
Figure 5: a detail on an enlarged scale of the embodiment according to Figure 3;
Figure 6: a cross-section through a third embodiment of a slide with guide tube;
Figure 7: a longitudinal section through the embodiment according to Figure 6;
Figure 8: part of the embodiment according to Figure 3 on an enlarged scale;
Figure 9: a cross-section through a fourth embodiment of a slide with guide tube;
Figure 10: a longitudinal section through the embodiment according to Figure 9;
Figure 11: part of the embodiment according to Figure 9 on an enlarged scale;
216~6~7 Figure 12: a radial section through a part of a first embodiment of a seal arrangement for use in a parallel slide gate valve of the abovementioned type, and Figure 13: a radial section through a part of a further embodiment of a seal arrangement for use in a parallel slide gate valve of the abovementioned type.
The paxallel slide gate valve illustrated in Figures 1 and 2 comprises a casing 13, having an inlet nozzle 16 and an outlet nozzle 18, and in which there is located a slide 21 containing two closure plates 1 and 2. Said slide is mov able transversely to the nozzles 16, 18 located on a common axis 24 between two oppositely-~.ying seat surfaces 14, 15. In addition, a guide tube 30 is provided, having two seal rings 31 and 32, which in the open position of the slide not shown here, may be pressed under the action of pressure medium against the seal seats 14, 15 of the slide casing 13. The seal rings 31, 32 are respectively integral components of the two closure plates 1 and 2. In the closed position of the slide 21 illustrated in Figures 1 and 2, the two closure plates 1 and 2 or their annular seal surfaces 25, 26 may also be pressed in a fluid-tight manner, under the action of a pressure medium introducible between the two closure plates 1 and 2, against the respectively associated casing seat surfaces 14, 15.
l0 216687 During actuation of the slide, said slide is under a lower internal pressure than in both end positions.
The space 28, 29 between the two closure plates 1, 2 and seal rings 31, 32 is sealed off from the environment on the one hand by a compensator 4 extending along the outer circumference, and on the other hand by a compensator 10 located between the passage 3 of the guide tube 30 and the unit comprising closure plate 2 and seal ring 32, which is axially movable thereto. The compensator 10 has a surrounding expansion bead, not shown in more detail in Figure 1, whereas the outer compensator 4 is formed by a one-piece or multiple-part metal strip, bent in a corrugated configuration, with a half-shaft extending over the circumference, which is welded fluid-tight along its two circumferential edges to the two closure plates 1, 2 or the seal rings 31, 32 integrally connected therewith. Pressure medium may be introduced into the abovementioned space 28, 29, either via a separate pressure medium pipe 8 or through a hollow spindle 6 in effective connection with a slide drive 33. The portion of the hollow spindle 6 opening into the space 28, 29 is identified by reference numeral 5.
A hose connection between the hollow spindle 6 and a pressure medium store not shown in detail is identified by reference numeral 9. The mechanical connection between the closure plates 1, 2 together with seal rings 31, 32 and the hollow spindle 6 is effected via an intermediate piece 7. The plates 1 and 2 are 11 216~fi~r engaged on this intermediate piece 7, while the hollow spindle 6 is rigidly connected to said intermediate piece 7.
By means of a spindle nut (not shown) which acts on the hollow spindle 6 and is rotatably driven, the hollow spindle 6 may be moved axially to and fro, thus carrying with it the slide 21 together with guide tube 30. This to-and-fro movement is shown by the double arrow 34.
Furthermore, the axial spreading movement of the two closure plates 1 and 2 under the action of a pressure medium introduced into the space 28, 29 under a pressure higher than the operating pressure, is indicated by the double arrow 35. This spreading movement is preferably effected with a resilient return movement of the compensators 4, 10, so that after pressure reduction in the space 28, 29 a minimum pressure of the seal surfaces of the two closure plates or seal rings of the guide tube on the casing seal seats is ensured. Accordingly, when the internal pressure is reduced, the slide may be displaced with minimum friction on the casing seal seats 14, 15 in the direction of double arrow 34.
In the central area of the sides facing one another of the two closure plates 1 and 2, there operate stiffening members in the form of spacer webs 36.
12 216~6g7 According to Figure 2, these spacer webs are located at right angles to one another radially within the surrounding annular seal surfaces 25, 26 of the two closure plates 1 and 2, and are welded respectively to only one closure plate, i.e. according to Figure 1 to the closure plate 1. In the transitional area between the two slide plates 1 and 2 on the one hand and the seal rings 32, 32 on the other hand, no spacer web 36 is necessary. In the case of larger dimensions, however, spacer webs 36 should be located in this transitional area. These spacer webs 36 also serve as stroke-limiters, i.e. they determine the maximum approach of the two closure plates 1, 2 or of the seal rings 31, 32 integrally connected with this for purposes of the translatory movement of the slide in the direction of the double arrow 34.
In the outer corner region of the guide tube 30, instead of spacer webs 36, spacer rods 37 are provided, which are respectively rigidly connected, particularly welded, to only one of the two seal rings. with reference to the arrangement of the spacer rods 37, reference is made to Figure 2.
In order to keep clean the casing 13 outwith the slide, particularly outwith the compensator 4, rinsing medium, particularly rinsing vapour, may be introduced into the casing 13. This is removed through a laterally attached nozzle 38. In this respect it has become apparent that even when rinsing is carried out in the closed condition with identical rinsing pressure and internal pressure on the guide tube, the seal force does not drop to zero, because the difference between lower operational pressure and higher internal pressure on the surface corresponding to the median seal diameter is still available. In the open position of the slide, in the same operational condition, the annular surface between the internal diameter of the casing seat and the median seal diameter is usable, with the pressure differential being the same. The layout of the parallel slide gate valve shown must accordingly correspond. An adapted rinsing procedure with a lower rinsing pressure reinforces the sealing effect.
When required, particularly when the internal pressure drops too far, in order to obtain sufficient sealing effect of the fitting in the closed position of the slide, the space 28, 29 is preferably still connected to the pressure side of the operation medium. Via two pipes 39', in each of which a non-return valve 22 is located, the internal pressure in the slide casing 12 may be adapted to the minimum pressure in the system.
The two pipes 39' are combined in front of the entry into the slide casing to form a common pipe 39, in which there is located a two-way magnetic valve 23.
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,..,~ 14 In the embodiment according to Figures 3 to 5, there serves as a stiffening member between the two closure plates 1 and 2 a stiffening ring 20, extending radially within the surrounding seal surfaces 25, 25, and welded to the inner side of the closure plate 1. The spacing of the two closure plates 1 and 2 together with the integrated seal rings 31, 32 of the guide tube 30 is effected by means of an external rectangular frame 17 which is welded to the closure plates 1 and 2 inclusive of the integrated seal rings 31, 32. The tubular passage 3 of the guide tube 30 is, according to Figure 5, welded to the closure plate 1 (annular weld seam 40 in Figure 5). Moreover, the passage 3 is movable in an axial direction relative to the other closure plate 2. Accordingly an annular slot 11 is formed between the passage 3 and the closure plate 2.
In order to keep the space 28, 29 between the two closure plates 1, 2 inclusive of integrated seal rings 31, 32 fluid-tight from the environment, there extends around the passage 3 a compensator 12 corresponding to the compensator 4 according to the embodiment in Figure 1. The compensator 12 is welded close to the passage 3 on the inner side both of the closure plate 1, together with integrated seal ring 31, and of the closure plate 2 together with integrated seal ring 32.
The corresponding annular weld seams are indicated in Figure 5 by reference numerals 41 and 42. The end face of the tubular passage 3 associated with the annular slot 11 is conically tapered in an inward direction.
15 21656~~
The dimensions of the annular slot 11 are small enough for it to operate as a seal.
The embodiment according to Figures 6 to 8 differs from that in Figures 3 to 5 on the one hand in that the closure plates 1 and 2 are provided in the central area of the sides facing one another respectively with a circular reinforcing plate 27. This ensures that, when a pressure medium is introduced into the space 28 between the two closure plates 1 and 2, substantially only a deformation is obtained of the annular seal surfaces 25, 26, said surfaces being in sealing contact on the associated casing seal seats. Above all however, it is ensured that, if the pressure medium fails in the closed position of the slide, the plate construction does not collapse inwards.
Further, the embodiment in Figures 6 to 8 differs from that in Figures 3 to 5 in that the compensator 12 extending about the passage 3 of guide tube 30 is welded to the closure plates 1 and 2 or integrated seal rings 31, 32 in such a way that welding may respectively be effected from the exterior. In this respect, reference is made to the annular weld seams 43, 44 in Figure 8. In order to obtain the abovementioned slot 11, there is provided at the level of the closure plate 2 between compensator 12 and passage 3 an additional spacer ring 45, which is welded to the compensator 12, preferably by means of the same 16 2~ 6567 annular weld seam 48 serving to provide a connection between compensator 12 and closure plate 2.
It should further be mentioned that the rectangular plate 17 is made of sheet metal strip. This sheet metal frame has the advantage that the passage 3 need no longer be sealed gas-tight from the operating medium. In addition, the compensator 4 may be omitted.
In the embodiment in Figures 9 to 11, the stiffening ring 20 is welded to the inner sides of both closure plates 1 and 2. The same applies to the tubular passage 3, as Figure 11 shows. Accordingly, the central space 28 between the two closure plates 1, 2, closed by the stiffening ring 20, is sealed. The pressure medium introduced through the hollow spindle 6 is only effective in the remaining space 29 between the closure plates 1 and seal rings 31, 32 integrally connected therewith, in such a way that the annular seal surfaces 25, 26 of the closure plates 1, 2 or the seal rings 31, 32 of the guide tube 30 are bulged axially outwards, as shown in dotted lines in Figure 9.
In this embodiment, compensators are omitted.
Moreover, it represents an extremely simple welded construction which may be produced from relatively thin-walled plates.
In order to avoid tensions at the edge of the transitional area between guide tube and shut-off 17 2.16687 portion, and in the corner area of the described box constructions, the peripheral contour of the slide box formed from the plates 1, 2 or seal rings 31, 32 and the rectangular frame 17 is formed in accordance with the contour of the annular seal surfaces 25, 26 and seal rings 31, 32. This preferred peripheral contour is shown in dashed-dotted lines in Figure 10 (contour line 46 in a spectacle shape).
There may be provided as required on the seal surfaces of the closure plates 1 and 2 and on the seal rings 31, 32, or alternatively on the casing seal seats 14, 15, separate seal arrangements with a seal ring, as will be described in more detail in the following with reference to Figures 12 and 13:
Figure 12 shows a portion of such a seal arrangement in radial section, i.e. in section through the axis of rotation of a tubular pipe or of a parallel slide gate valve of the type already described; as a variation to the embodiments already described, the slide casing is identified by the reference number 110, the slide plate by number 103 and the axis of rotation of the tubular pipe or of the nozzles 16, 18 in Figure 1 by the number 104. The to-and-fro movement of the slide 300 is indicated by the double arrow 117.
The seal arrangement associated with the slide 103 comprises a seal ring 102, extending around the axis of rotation 104, and made of highly wear-resistant seal material. The side of the seal ring 102 facing the slide 103 is flattened, forming a surrounding seal surface 106. The seal ring 102 is embedded in a surrounding groove-like recess 118 of a multi-layer or multi-coating (105 layers), resiliently elastic diaphragm 101, and is movable under the action of a pressure medium loading the diaphragm 101, with its seal surface 106 in the seal position, i.e. against the slide 103. There is preferably located on both sides of the slide 103, i.e. at both casing seal seats, a seal arrangement of the type illustrated, so that a seal of the tubular pipe is ensured not only at the side of lower pressure but also at the side of higher pressure on the slide 103.
The diaphragm 101 is connected in a fluid-tight manner, i.e. welded (annular weld seams 107) along its internal and external edge with the casing 111, in such a way that a likewise surrounding pressure medium space 114, 115 is defined between the diaphragm 101 on one hand and the casing 111 on the other hand, said space 114, 115 being in a fluid connection via a pressure medium pipe 108 with a pressure medium store 109.
In the region of the annular weld seams 107, the diaphragm 101 is reinforced by additional, respectively surrounding strips of material 119, 120 (along the internal edge of the diaphragm) or 121, 122 (along the 19 216~6~'~
outer edge of the diaphragm), in order to enable compensation for the increased bending moments occurring in these areas. The cross-section of the diaphragm 101 is approximately U-shaped, both legs being respectively bent outwards so that they extend approximately parallel to the seal surface 106 of the seal ring 102. In a corresponding way, the annular surface of the casing 111 facing the diaphragm is formed so that the diaphragm 101 together with seal ring 102 are accommodated in a flush, countersunk manner, a surrounding pressure medium space resulting, in the unloaded condition of the diaphragm, between said diaphragm and the said annular space 123, respectively in the region of the base of the surrounding recess 118, and also in the bending area of the two legs of the diaphragm. These pressure medium spaces are identified by the reference numerals 115 or 114.
Figure 12 also shows that the surrounding recess 118 of diaphragm 101 is guided in a corresponding surrounding recess 124 of the associated annular surface 123 of the casing 111 in the direction of movement of the seal ring 102; the direction of movement of the seal ring 102 is shown in Figure 1 by the double arrow 125. This axial guidance is effected in the region of an inner and outer surrounding contact edge 116 between the diaphragm 101 and the inner and outer lateral limit of the recess 124 in the casing 111. This contact edge is ~~65687 raised, producing a fluid connection between the pressure medium spaces 114 and 125, when it is necessary to press the seal ring 102 under increased pressure against the shut-off unit 103, particularly on the side of higher pressure of the shut-off unit; for on the side of lower pressure, the shut-off unit is in any case pressed by the pressure medium pressure against the seal surface 106 of the associated seal ring 102, i.e. located on the side of lower pressure.
Thus, at an extremely high pressure of the operating medium, the seal ring 102 may be pressed so hard into the casing recess 124 that the diaphragm 102 is totally in contact over its entire length and width with the casing annular surface 123. The volume of the pressure medium spaces 114, 115 is reduced to almost zero. It is advantageous in that case that, despite the great forces acting on the seal ring 102, the diaphragm 101 is subjected to no further deformation. Nor are the annular weld~seams 107 further stressed. The life expectancy of the seal arrangement described is accordingly high.
In Figure 12, the pressure transmission diaphragm 101 is shown in the unloaded condition. In this condition, the spacing 113 between the seal surface 106 of the seal ring 102 and the associated surface of the shut-off unit 103 is approximately equal to the maximum space 112 between the diaphragm 101 and the deepest point of the casing recess 124. In this way approximately identical pressures may be generated in the diaphragm with a different preceding sign.
Simultaneously, without pressure increase in the pressure medium space 115, minimum seal force of the seal ring 102 is ensured, due only to the spring resilience of the diaphragm 101. Moreover, only extremely small volume changes of the pressure medium in the pressure medium store 109 are necessary in order to obtain the respective end positions of the diaphragm or of the seal ring 102 embedded in the diaphragm.
volume differences due to changes in operating temperature are equalised in that the pressure medium container 109 is designed as an expanding container or vessel, preferably in a bellows configuration. The pressure of pressure medium is preferably generated purely mechanically, e.g. by means of a weight 110. A
spring may also be provided instead of a weight.
Alternatively, it is also possible to place the pressure medium 109 under hydraulic or pneumatic pressure. The first- mentioned weight 110 has the advantage that the pressure of pressure medium remains substantially constant independently of the operating temperature due to the expansion facility of the pressure medium container 109. A fluid medium is preferably used as a pressure medium.
When the seal arrangement described is located on the pressure side of a shut-off unit, leakages are also reliably avoided at that point. The pressure of the seal ring 102 is effected in dependence on the pressure of the pressure medium. The seal arrangement described is thus adjustable in dependence on external conditions.
In order to avoid the arrangement of the material strips 119, 120 or 121, 122 reinforcing the two edges of the diaphragm 101, it is proposed according to Figure 13 that there should connect to both sides of the groove-like recess 118 of the multi-layer diaphragm 101 respectively a rotating shaft 106 (radially inwards) and 127 (radially outwards) with an approximately S-shaped cross-section, in such a way that the inner and outer edge of the diaphragm 101 extend respectively approximately parallel to the direction of movement 125 of the seal ring 102. Thus lateral tensions on the diaphragm can be reduced to a minimum without impairing the flexibility of the same.
The annular surface 123 of the casing 111 facing the diaphragm 101 is naturally also formed in a corresponding way. In radial section, the latter has a contour corresponding to that of the diaphragm 101.
Thus in turn the same effects and advantages can be obtained as are described with reference to the embodiment in Figure 12.
The individual material strips from which the diaphragm 101 is built, are made from metal which is resistant to high temperatures and also remains sufficiently resiliently elastic at high temperatures. In the unloaded condition of the diaphragm, the material strips are in close contact with one another over their entire length and width. Thus the degree of effectiveness of the pressure transformation already mentioned is additionally improved. Deformation energy due to slots between the individual layers of the diaphragm is avoided.
The abovementioned load 110 acting on the pressure medium store 109 is coupled to the drive system and dead stroke of the shut-off unit 103 in such a way that, upon actuation of the same, loading is removed from the pressure medium store 109. This ensures a desirable ease of running of the shut-off unit 103 upon its movement from the closed position into the opening position and vice versa.
It should also be noted in relation to the embodiment in Figure 13, that, due to the S-shaped curved contour of the inner and outer edge of the diaphragm 101, the area of maximum tension is displaced away from the annular weld seams 107 into the area of the first arc of the diaphragm 101 connecting respectively to the annular weld seam 107.
In Figure 13 a minimum space 105 is shown between the diaphragm 111 and the shut-off unit 103, which must be maintained in the unloaded condition, i.e. in the ~1~5~g7 moving position of the shut-off unit 103, taking into account the maximum wear on the seal surface 106, in order to avoid direct contact between diaphragm 101 and shut-off unit 103.
It should also be mentioned that the pressure medium spaces 114 formed on both sides of the seal ring 102, are originally free of pressure medium. Pressure medium passes into these spaces 114 only when pressure medium passes through the surrounding contact edges 116. Excess pressure medium escapes through this area, out of the surrounding pressure medium spaces 114 into the surrounding pressure medium space 115, which is in a fluid connection with the pressure medium pipe 108.
It would also be imaginable to connect the pressure medium spaces 114 formed on both sides of the seal ring 102 with the pressure medium pipe 108, interposing a two-way valve, so that the pressure medium spaces may be separately charged if necessary.
All the features disclosed in the Application Documents are claimed as essential to the invention, insofar as, individually or in combination, they are new in comparison to prior art.
LIST OF REFERENCE NITMERALS
1 closure plate 2 closure plate 3 passage 4 compensator 5 hollow spindle portion 6 hollow spindle 7 intermediate piece 8 pipe 9 hose pipe 10 compensator 11 annular slot 12 compensator 13 casing 14 seat surface 15 seat surface 16 inlet nozzle 17 rectangular frame 18 outlet nozzle 20 reinforcing ring 21 slide 22 non-return valve 23 magnetic valve 26 216568' 24 axis 25 seal surface 26 seal surface 27 reinforcing plate 28 space 29 space (annular space?
The invention relates to a parallel slide gate valve with a casing having an inlet nozzle and an outlet nozzle, and in which there is located a slide containing two closure plates, said slide being movable transversely to the nozzles which are located on a common axis, between two oppositely-lying seat surfaces, both closure plates or their seal surfaces, in the closed position, being in sealing contact with the respectively associated seat surface under the action of a pressure medium introducible between the two closure plates or seal surfaces.
Such a parallel slide gate valve is generally known, particularly in the form of a so-called guide tube shutter. In this respect, reference is made to EP 0 326 787 B1, and to DE 40 11 274 C.
The object of the known constructions is that the parallel slide gate valve, while maintaining a good sealing function in its closed position, is subject during the opening and closing movement of the slide to only limited frictional forces on the seat and seal surfaces. This purpose is only partly fulfilled in the guide tube shutter according to DE 40 11 274 C, i.e.
only in the region of the guide tube. The spreading 2 2~ 6568' movement of the closure plates is effected purely mechanically, i.e. using the so-called 'wedge-in-wedge' principle. The problem arises here that, upon opening the fitting, specific return movement of the two closure plates is effected by means of separate plate spring assemblies. Accordingly, an uncontrolled adhesive friction arises between the seal surfaces of the closure plates on the one hand and the casing seal seats and the so-called guide plates on the other hand, resulting in a correspondingly high abrasive stress on the seal surfaces. Moreover, plate spring assemblies integrated in the actuating rod are necessary, in order to control the °wedge-in-wedge~~ mechanism.
The construction according to EP 0 326 787 B1 is extremely expensive and in addition'extremely heavy in construction. The closure plates fill practically the entire slot between the casing seal seats.
The purpose underlying the present invention is to provide a parallel slide gate valve of the type already mentioned, which is characterised on the one hand by a highly efficient sealing effect and on the other hand by minimum friction upon movement of the slide in the open position and vice versa, and by an extremely lightweight construction, and which adapts simply to deformations in the casing and thus in the seal seats.
.~ 3 2I6~~
8~
This purpose is fulfilled according to the invention by the characterising features of Patent claim 1.
Due to the claimed stiffening of the slide, relatively thin-walled closure plates may be used, which in an extreme case deform axially under the action of a pressure medium, with a corresponding contact on the casing seal seat in the closed position of the slide.
In this lightweight construction it is also possible to reduce the sealing force by reducing the pressure of the pressure medium in such a way that the slide may be operated, even at larger dimensions, with relatively low propulsive force. The thin-walled construction finally permits adaptation~of the slide to deformations of the casing or casing seal seats. Unacceptable deformation, particularly recessing in the closed position of the slide, is prevented by means of the stiffening members which are effective in the central area of the closure plates.
According to claim 2, there may serve as stiffening members either spacer webs located between the closure plates, or a stiffening ring, located between the closure plates, and extending radially within the surrounding seal surfaces of the two closure plates.
The same applies also with regard to the position of the mentioned spacer webs. These stiffening members simultaneously limit the maximum approach of the two closure plates upon opening of the fitting. For functional reasons they are also located only on the inner side of one of the two closure plates, in particular by welding.
Alternatively, stiffening of the closure plates in the central area may be effected by stiffening plates, preferably circular in shape, located on the sides facing one another.
Finally, it is also feasible in accordance with claim 2 to provide a stiffening ring, which is securely cannected, particularly welded, to both closure plates, so that there is formed on the one hand an annular space associated with the seal surfaces, and on the other hand a space formed within the stiffening ring, which is not in fluid connection with the other annular space. Only the outer annular space, which is associated with the seal surfaces of the two closure plates, communicates with a source of pressure medium and thus may be loaded by pressure medium with a consequent axial deformation, i.e. bulging of the seal surfaces in the closed position of the slide, so that the seal surfaces may be pressed against the seat surfaces of the casing.
In the variants with central stiffening plates or with stiffening members attached only on the inner side of a Closure plate, the two closure plates are, in all, movable relative to one another in an axial direction 2i6~fi8'~
under the action of a pressure medium, the space between the two closure plates being restricted in a fluid-tight manner from the environment by compensators extending along the outer circumference. Such a compensator is preferably formed by a pipe section, produced from a strip of metal bent in a corrugated manner, with at least one half-shaft extending over the circumference, said pipe section being welded fluid-tight along both its peripheral edges to the two closure plates, a pressure medium pipe opening through the corrugated pipe section into the space between the two closure plates.
The construction according to the invention is particularly suitable also for a parallel slide gate valve which additionally comprises a so-called guide tube (= guide tube shutter, or also named pipe bridge valve), which has two seal rings which, in the open position of the slide, may be pressed under the action of pressure medium against the seal seats of the slide casing, the pressure medium space associated with the seal rings of the guide tube being connected in fluid terms with the pressure medium space associated with the seal surfaces of the two closure plates. Thus one and the same pressure medium, or the same pressure medium unit, may be used both for pressing the seal rings of the guide tube and pressing the seal surfaces of the two closure plates.
A simple construction of the last-named embodiment is characterised in that the two closure plates of the slide and the two seal rings of the guide tube are respectively integrally connected together, i.e. form integral plate portions, the space between the two plate portions being closed fluid-tight from the environment at the edges, particularly by means of a compensator of the abovementioned type. The closure plates and seal rings then form part of a fluid-tight closed box, whose variable height is determined by the compensators mentioned. The corners of the said box are rounded in accordance with the contour of the seal surfaces of the closure plates or seal rings of the guide tubes. In this way minimum pressures are obtained on the closure plates and seal rings of the guide tube itself as well as in the transitional area between closure plates and seal rings when the latter are pressed against the casing seal seats.
In order to ensure a sufficient seal effect of the fluid medium duct in the closed position of the slide even upon failure of the pressure medium unit for the axial spreading of the closure plates, the pressure medium space between the seal surfaces of the closure plates in the closed position of the slide may be connected with the pressure side of the casing or its flow passage, so that the said pressure medium space is under system pressure. This is a safety feature not to be underestimated; only the gaseous components of the ' 21~~687 operating medium being used of course for this purpose.
During actuation, the internal pressure in the fluid-tight closed box is reduced, in order to obtain easy-running displacement of the shut-off member with or without guide tubes. Should unforeseen leaks occur, by means of introduction of rinsing medium, particularly rinsing vapour into the slide casing, the penetration of operating medium into the slide casing, contaminating the fitting within the casing, is avoided.
Claims 12 to 21 relate to a special seal arrangement for slide and guide tube, which is recommended for parallel slide gate valves of the type in question here especially when high pressures and temperatures are to be controlled.
Embodiments of the parallel slide gate valve according to the invention will be explained in more detail in the following with reference to the annexed drawings, which show:
Figure 1: a cross-section through a first embodiment of a parallel slide gate valve with guide tube;
Figure 2: a view, partially in side elevation, partially in longitudinal section, of the embodiment according to Figure 1;
Figure 3: a cross-section through a second embodiment of a slide with guide tube;
Figure 4: a longitudinal section through the embodiment according to Figure 3;
Figure 5: a detail on an enlarged scale of the embodiment according to Figure 3;
Figure 6: a cross-section through a third embodiment of a slide with guide tube;
Figure 7: a longitudinal section through the embodiment according to Figure 6;
Figure 8: part of the embodiment according to Figure 3 on an enlarged scale;
Figure 9: a cross-section through a fourth embodiment of a slide with guide tube;
Figure 10: a longitudinal section through the embodiment according to Figure 9;
Figure 11: part of the embodiment according to Figure 9 on an enlarged scale;
216~6~7 Figure 12: a radial section through a part of a first embodiment of a seal arrangement for use in a parallel slide gate valve of the abovementioned type, and Figure 13: a radial section through a part of a further embodiment of a seal arrangement for use in a parallel slide gate valve of the abovementioned type.
The paxallel slide gate valve illustrated in Figures 1 and 2 comprises a casing 13, having an inlet nozzle 16 and an outlet nozzle 18, and in which there is located a slide 21 containing two closure plates 1 and 2. Said slide is mov able transversely to the nozzles 16, 18 located on a common axis 24 between two oppositely-~.ying seat surfaces 14, 15. In addition, a guide tube 30 is provided, having two seal rings 31 and 32, which in the open position of the slide not shown here, may be pressed under the action of pressure medium against the seal seats 14, 15 of the slide casing 13. The seal rings 31, 32 are respectively integral components of the two closure plates 1 and 2. In the closed position of the slide 21 illustrated in Figures 1 and 2, the two closure plates 1 and 2 or their annular seal surfaces 25, 26 may also be pressed in a fluid-tight manner, under the action of a pressure medium introducible between the two closure plates 1 and 2, against the respectively associated casing seat surfaces 14, 15.
l0 216687 During actuation of the slide, said slide is under a lower internal pressure than in both end positions.
The space 28, 29 between the two closure plates 1, 2 and seal rings 31, 32 is sealed off from the environment on the one hand by a compensator 4 extending along the outer circumference, and on the other hand by a compensator 10 located between the passage 3 of the guide tube 30 and the unit comprising closure plate 2 and seal ring 32, which is axially movable thereto. The compensator 10 has a surrounding expansion bead, not shown in more detail in Figure 1, whereas the outer compensator 4 is formed by a one-piece or multiple-part metal strip, bent in a corrugated configuration, with a half-shaft extending over the circumference, which is welded fluid-tight along its two circumferential edges to the two closure plates 1, 2 or the seal rings 31, 32 integrally connected therewith. Pressure medium may be introduced into the abovementioned space 28, 29, either via a separate pressure medium pipe 8 or through a hollow spindle 6 in effective connection with a slide drive 33. The portion of the hollow spindle 6 opening into the space 28, 29 is identified by reference numeral 5.
A hose connection between the hollow spindle 6 and a pressure medium store not shown in detail is identified by reference numeral 9. The mechanical connection between the closure plates 1, 2 together with seal rings 31, 32 and the hollow spindle 6 is effected via an intermediate piece 7. The plates 1 and 2 are 11 216~fi~r engaged on this intermediate piece 7, while the hollow spindle 6 is rigidly connected to said intermediate piece 7.
By means of a spindle nut (not shown) which acts on the hollow spindle 6 and is rotatably driven, the hollow spindle 6 may be moved axially to and fro, thus carrying with it the slide 21 together with guide tube 30. This to-and-fro movement is shown by the double arrow 34.
Furthermore, the axial spreading movement of the two closure plates 1 and 2 under the action of a pressure medium introduced into the space 28, 29 under a pressure higher than the operating pressure, is indicated by the double arrow 35. This spreading movement is preferably effected with a resilient return movement of the compensators 4, 10, so that after pressure reduction in the space 28, 29 a minimum pressure of the seal surfaces of the two closure plates or seal rings of the guide tube on the casing seal seats is ensured. Accordingly, when the internal pressure is reduced, the slide may be displaced with minimum friction on the casing seal seats 14, 15 in the direction of double arrow 34.
In the central area of the sides facing one another of the two closure plates 1 and 2, there operate stiffening members in the form of spacer webs 36.
12 216~6g7 According to Figure 2, these spacer webs are located at right angles to one another radially within the surrounding annular seal surfaces 25, 26 of the two closure plates 1 and 2, and are welded respectively to only one closure plate, i.e. according to Figure 1 to the closure plate 1. In the transitional area between the two slide plates 1 and 2 on the one hand and the seal rings 32, 32 on the other hand, no spacer web 36 is necessary. In the case of larger dimensions, however, spacer webs 36 should be located in this transitional area. These spacer webs 36 also serve as stroke-limiters, i.e. they determine the maximum approach of the two closure plates 1, 2 or of the seal rings 31, 32 integrally connected with this for purposes of the translatory movement of the slide in the direction of the double arrow 34.
In the outer corner region of the guide tube 30, instead of spacer webs 36, spacer rods 37 are provided, which are respectively rigidly connected, particularly welded, to only one of the two seal rings. with reference to the arrangement of the spacer rods 37, reference is made to Figure 2.
In order to keep clean the casing 13 outwith the slide, particularly outwith the compensator 4, rinsing medium, particularly rinsing vapour, may be introduced into the casing 13. This is removed through a laterally attached nozzle 38. In this respect it has become apparent that even when rinsing is carried out in the closed condition with identical rinsing pressure and internal pressure on the guide tube, the seal force does not drop to zero, because the difference between lower operational pressure and higher internal pressure on the surface corresponding to the median seal diameter is still available. In the open position of the slide, in the same operational condition, the annular surface between the internal diameter of the casing seat and the median seal diameter is usable, with the pressure differential being the same. The layout of the parallel slide gate valve shown must accordingly correspond. An adapted rinsing procedure with a lower rinsing pressure reinforces the sealing effect.
When required, particularly when the internal pressure drops too far, in order to obtain sufficient sealing effect of the fitting in the closed position of the slide, the space 28, 29 is preferably still connected to the pressure side of the operation medium. Via two pipes 39', in each of which a non-return valve 22 is located, the internal pressure in the slide casing 12 may be adapted to the minimum pressure in the system.
The two pipes 39' are combined in front of the entry into the slide casing to form a common pipe 39, in which there is located a two-way magnetic valve 23.
,A
,..,~ 14 In the embodiment according to Figures 3 to 5, there serves as a stiffening member between the two closure plates 1 and 2 a stiffening ring 20, extending radially within the surrounding seal surfaces 25, 25, and welded to the inner side of the closure plate 1. The spacing of the two closure plates 1 and 2 together with the integrated seal rings 31, 32 of the guide tube 30 is effected by means of an external rectangular frame 17 which is welded to the closure plates 1 and 2 inclusive of the integrated seal rings 31, 32. The tubular passage 3 of the guide tube 30 is, according to Figure 5, welded to the closure plate 1 (annular weld seam 40 in Figure 5). Moreover, the passage 3 is movable in an axial direction relative to the other closure plate 2. Accordingly an annular slot 11 is formed between the passage 3 and the closure plate 2.
In order to keep the space 28, 29 between the two closure plates 1, 2 inclusive of integrated seal rings 31, 32 fluid-tight from the environment, there extends around the passage 3 a compensator 12 corresponding to the compensator 4 according to the embodiment in Figure 1. The compensator 12 is welded close to the passage 3 on the inner side both of the closure plate 1, together with integrated seal ring 31, and of the closure plate 2 together with integrated seal ring 32.
The corresponding annular weld seams are indicated in Figure 5 by reference numerals 41 and 42. The end face of the tubular passage 3 associated with the annular slot 11 is conically tapered in an inward direction.
15 21656~~
The dimensions of the annular slot 11 are small enough for it to operate as a seal.
The embodiment according to Figures 6 to 8 differs from that in Figures 3 to 5 on the one hand in that the closure plates 1 and 2 are provided in the central area of the sides facing one another respectively with a circular reinforcing plate 27. This ensures that, when a pressure medium is introduced into the space 28 between the two closure plates 1 and 2, substantially only a deformation is obtained of the annular seal surfaces 25, 26, said surfaces being in sealing contact on the associated casing seal seats. Above all however, it is ensured that, if the pressure medium fails in the closed position of the slide, the plate construction does not collapse inwards.
Further, the embodiment in Figures 6 to 8 differs from that in Figures 3 to 5 in that the compensator 12 extending about the passage 3 of guide tube 30 is welded to the closure plates 1 and 2 or integrated seal rings 31, 32 in such a way that welding may respectively be effected from the exterior. In this respect, reference is made to the annular weld seams 43, 44 in Figure 8. In order to obtain the abovementioned slot 11, there is provided at the level of the closure plate 2 between compensator 12 and passage 3 an additional spacer ring 45, which is welded to the compensator 12, preferably by means of the same 16 2~ 6567 annular weld seam 48 serving to provide a connection between compensator 12 and closure plate 2.
It should further be mentioned that the rectangular plate 17 is made of sheet metal strip. This sheet metal frame has the advantage that the passage 3 need no longer be sealed gas-tight from the operating medium. In addition, the compensator 4 may be omitted.
In the embodiment in Figures 9 to 11, the stiffening ring 20 is welded to the inner sides of both closure plates 1 and 2. The same applies to the tubular passage 3, as Figure 11 shows. Accordingly, the central space 28 between the two closure plates 1, 2, closed by the stiffening ring 20, is sealed. The pressure medium introduced through the hollow spindle 6 is only effective in the remaining space 29 between the closure plates 1 and seal rings 31, 32 integrally connected therewith, in such a way that the annular seal surfaces 25, 26 of the closure plates 1, 2 or the seal rings 31, 32 of the guide tube 30 are bulged axially outwards, as shown in dotted lines in Figure 9.
In this embodiment, compensators are omitted.
Moreover, it represents an extremely simple welded construction which may be produced from relatively thin-walled plates.
In order to avoid tensions at the edge of the transitional area between guide tube and shut-off 17 2.16687 portion, and in the corner area of the described box constructions, the peripheral contour of the slide box formed from the plates 1, 2 or seal rings 31, 32 and the rectangular frame 17 is formed in accordance with the contour of the annular seal surfaces 25, 26 and seal rings 31, 32. This preferred peripheral contour is shown in dashed-dotted lines in Figure 10 (contour line 46 in a spectacle shape).
There may be provided as required on the seal surfaces of the closure plates 1 and 2 and on the seal rings 31, 32, or alternatively on the casing seal seats 14, 15, separate seal arrangements with a seal ring, as will be described in more detail in the following with reference to Figures 12 and 13:
Figure 12 shows a portion of such a seal arrangement in radial section, i.e. in section through the axis of rotation of a tubular pipe or of a parallel slide gate valve of the type already described; as a variation to the embodiments already described, the slide casing is identified by the reference number 110, the slide plate by number 103 and the axis of rotation of the tubular pipe or of the nozzles 16, 18 in Figure 1 by the number 104. The to-and-fro movement of the slide 300 is indicated by the double arrow 117.
The seal arrangement associated with the slide 103 comprises a seal ring 102, extending around the axis of rotation 104, and made of highly wear-resistant seal material. The side of the seal ring 102 facing the slide 103 is flattened, forming a surrounding seal surface 106. The seal ring 102 is embedded in a surrounding groove-like recess 118 of a multi-layer or multi-coating (105 layers), resiliently elastic diaphragm 101, and is movable under the action of a pressure medium loading the diaphragm 101, with its seal surface 106 in the seal position, i.e. against the slide 103. There is preferably located on both sides of the slide 103, i.e. at both casing seal seats, a seal arrangement of the type illustrated, so that a seal of the tubular pipe is ensured not only at the side of lower pressure but also at the side of higher pressure on the slide 103.
The diaphragm 101 is connected in a fluid-tight manner, i.e. welded (annular weld seams 107) along its internal and external edge with the casing 111, in such a way that a likewise surrounding pressure medium space 114, 115 is defined between the diaphragm 101 on one hand and the casing 111 on the other hand, said space 114, 115 being in a fluid connection via a pressure medium pipe 108 with a pressure medium store 109.
In the region of the annular weld seams 107, the diaphragm 101 is reinforced by additional, respectively surrounding strips of material 119, 120 (along the internal edge of the diaphragm) or 121, 122 (along the 19 216~6~'~
outer edge of the diaphragm), in order to enable compensation for the increased bending moments occurring in these areas. The cross-section of the diaphragm 101 is approximately U-shaped, both legs being respectively bent outwards so that they extend approximately parallel to the seal surface 106 of the seal ring 102. In a corresponding way, the annular surface of the casing 111 facing the diaphragm is formed so that the diaphragm 101 together with seal ring 102 are accommodated in a flush, countersunk manner, a surrounding pressure medium space resulting, in the unloaded condition of the diaphragm, between said diaphragm and the said annular space 123, respectively in the region of the base of the surrounding recess 118, and also in the bending area of the two legs of the diaphragm. These pressure medium spaces are identified by the reference numerals 115 or 114.
Figure 12 also shows that the surrounding recess 118 of diaphragm 101 is guided in a corresponding surrounding recess 124 of the associated annular surface 123 of the casing 111 in the direction of movement of the seal ring 102; the direction of movement of the seal ring 102 is shown in Figure 1 by the double arrow 125. This axial guidance is effected in the region of an inner and outer surrounding contact edge 116 between the diaphragm 101 and the inner and outer lateral limit of the recess 124 in the casing 111. This contact edge is ~~65687 raised, producing a fluid connection between the pressure medium spaces 114 and 125, when it is necessary to press the seal ring 102 under increased pressure against the shut-off unit 103, particularly on the side of higher pressure of the shut-off unit; for on the side of lower pressure, the shut-off unit is in any case pressed by the pressure medium pressure against the seal surface 106 of the associated seal ring 102, i.e. located on the side of lower pressure.
Thus, at an extremely high pressure of the operating medium, the seal ring 102 may be pressed so hard into the casing recess 124 that the diaphragm 102 is totally in contact over its entire length and width with the casing annular surface 123. The volume of the pressure medium spaces 114, 115 is reduced to almost zero. It is advantageous in that case that, despite the great forces acting on the seal ring 102, the diaphragm 101 is subjected to no further deformation. Nor are the annular weld~seams 107 further stressed. The life expectancy of the seal arrangement described is accordingly high.
In Figure 12, the pressure transmission diaphragm 101 is shown in the unloaded condition. In this condition, the spacing 113 between the seal surface 106 of the seal ring 102 and the associated surface of the shut-off unit 103 is approximately equal to the maximum space 112 between the diaphragm 101 and the deepest point of the casing recess 124. In this way approximately identical pressures may be generated in the diaphragm with a different preceding sign.
Simultaneously, without pressure increase in the pressure medium space 115, minimum seal force of the seal ring 102 is ensured, due only to the spring resilience of the diaphragm 101. Moreover, only extremely small volume changes of the pressure medium in the pressure medium store 109 are necessary in order to obtain the respective end positions of the diaphragm or of the seal ring 102 embedded in the diaphragm.
volume differences due to changes in operating temperature are equalised in that the pressure medium container 109 is designed as an expanding container or vessel, preferably in a bellows configuration. The pressure of pressure medium is preferably generated purely mechanically, e.g. by means of a weight 110. A
spring may also be provided instead of a weight.
Alternatively, it is also possible to place the pressure medium 109 under hydraulic or pneumatic pressure. The first- mentioned weight 110 has the advantage that the pressure of pressure medium remains substantially constant independently of the operating temperature due to the expansion facility of the pressure medium container 109. A fluid medium is preferably used as a pressure medium.
When the seal arrangement described is located on the pressure side of a shut-off unit, leakages are also reliably avoided at that point. The pressure of the seal ring 102 is effected in dependence on the pressure of the pressure medium. The seal arrangement described is thus adjustable in dependence on external conditions.
In order to avoid the arrangement of the material strips 119, 120 or 121, 122 reinforcing the two edges of the diaphragm 101, it is proposed according to Figure 13 that there should connect to both sides of the groove-like recess 118 of the multi-layer diaphragm 101 respectively a rotating shaft 106 (radially inwards) and 127 (radially outwards) with an approximately S-shaped cross-section, in such a way that the inner and outer edge of the diaphragm 101 extend respectively approximately parallel to the direction of movement 125 of the seal ring 102. Thus lateral tensions on the diaphragm can be reduced to a minimum without impairing the flexibility of the same.
The annular surface 123 of the casing 111 facing the diaphragm 101 is naturally also formed in a corresponding way. In radial section, the latter has a contour corresponding to that of the diaphragm 101.
Thus in turn the same effects and advantages can be obtained as are described with reference to the embodiment in Figure 12.
The individual material strips from which the diaphragm 101 is built, are made from metal which is resistant to high temperatures and also remains sufficiently resiliently elastic at high temperatures. In the unloaded condition of the diaphragm, the material strips are in close contact with one another over their entire length and width. Thus the degree of effectiveness of the pressure transformation already mentioned is additionally improved. Deformation energy due to slots between the individual layers of the diaphragm is avoided.
The abovementioned load 110 acting on the pressure medium store 109 is coupled to the drive system and dead stroke of the shut-off unit 103 in such a way that, upon actuation of the same, loading is removed from the pressure medium store 109. This ensures a desirable ease of running of the shut-off unit 103 upon its movement from the closed position into the opening position and vice versa.
It should also be noted in relation to the embodiment in Figure 13, that, due to the S-shaped curved contour of the inner and outer edge of the diaphragm 101, the area of maximum tension is displaced away from the annular weld seams 107 into the area of the first arc of the diaphragm 101 connecting respectively to the annular weld seam 107.
In Figure 13 a minimum space 105 is shown between the diaphragm 111 and the shut-off unit 103, which must be maintained in the unloaded condition, i.e. in the ~1~5~g7 moving position of the shut-off unit 103, taking into account the maximum wear on the seal surface 106, in order to avoid direct contact between diaphragm 101 and shut-off unit 103.
It should also be mentioned that the pressure medium spaces 114 formed on both sides of the seal ring 102, are originally free of pressure medium. Pressure medium passes into these spaces 114 only when pressure medium passes through the surrounding contact edges 116. Excess pressure medium escapes through this area, out of the surrounding pressure medium spaces 114 into the surrounding pressure medium space 115, which is in a fluid connection with the pressure medium pipe 108.
It would also be imaginable to connect the pressure medium spaces 114 formed on both sides of the seal ring 102 with the pressure medium pipe 108, interposing a two-way valve, so that the pressure medium spaces may be separately charged if necessary.
All the features disclosed in the Application Documents are claimed as essential to the invention, insofar as, individually or in combination, they are new in comparison to prior art.
LIST OF REFERENCE NITMERALS
1 closure plate 2 closure plate 3 passage 4 compensator 5 hollow spindle portion 6 hollow spindle 7 intermediate piece 8 pipe 9 hose pipe 10 compensator 11 annular slot 12 compensator 13 casing 14 seat surface 15 seat surface 16 inlet nozzle 17 rectangular frame 18 outlet nozzle 20 reinforcing ring 21 slide 22 non-return valve 23 magnetic valve 26 216568' 24 axis 25 seal surface 26 seal surface 27 reinforcing plate 28 space 29 space (annular space?
30 guide tube 31 seal ring 32 seal ring ZO 33 slide drive 34 double arrow 36 spacer webs 37 spacer rods 38 nozzle 39 pipe 39~ pipe 40 annular weld seam 41 annular weld seam 42 annular weld seam 43 annular weld seam 44 annular weld seam 45 annular weld seam 46 contour line 101 pressure transmission diaphragm 102 seal ring 103 slide 104 axis of rotation 105 minimum space between diaphragm 101 and slide 103 in the movement position of the same 27 216~~87 106 seal surface 107 annular weld seam 108 pressure medium pipe 109 pressure medium store 110 load 111 casing 112 space 113 space 114 pressure medium space 115 pressure medium space 116 surrounding contact line as axial guide for the diaphragm 117 double arrow 118 surrounding recess 119- material 122 strips 123 annular surface 124 surrounding recess 125 double arrow
Claims (25)
1. A parallel slide gate valve apparatus including a casing having an inlet nozzle and an outlet nozzle in aligned spaced relation, each said nozzle having an end sealing surface, a slide having two thin-wall closure plates including an inlet seal plate and an outlet seal place, said inlet seal plate and said outlet seal plate being slidably mounted in parallel relationship within the space between and in opposed relation to said inlet nozzle and outlet nozzle respectively, each of said closure plates having a deflecting outer seal portion including an outer sealing surface configured to be aligned with said end sealing surface of said opposed nozzle and configured to be deflected into sealing engagement therewith by introduction of a pressure medium between the two closure thin-wall plates with said pressure medium applied to said outer seal portions, and at least one reinforcing assembly secured to at least one of said closure plates in a generally central portion of the closure plates and spaced inwardly of said outer seal portions, said reinforcing assembly supporting and stiffening the central portion of at least one of said thin-wall closure plates in the presence of said pressure medium and with said medium applied to the outer seal portions and thereby deflecting and moving the outer seal portions into firm improved sealing engagement between said sealing surface of the seal portions and said aligned opposed sealing surface of said opposed nozzles.
2. The parallel slide gate valve of Claim 1 wherein the said reinforcing assembly includes spacer webs secured to the closures plates.
3. The parallel slide gate valve of Claim 1 wherein said reinforcing assembly includes a ring secured between the closure plates.
4. The parallel slide gate valve of claim 1 wherein said reinforcing webs include a plurality of individual members located between the closure plates.
5. The parallel slide gate valve of claim 4 wherein said seal portions of said closure plates being spaced about the peripheral portion of said plates in alignment with said nozzles, and said members extend in angular relationship to form a substantial support inwardly of said seal surfaces.
6. The parallel slide gate valve of claim 1 wherein said reinforcing assembly includes first and second reinforcing plates secured one each to the central portion of each said closure plates, said reinforcing plates being secured on the opposing sides of said closure plates and in alignment with each other.
7. The parallel slide gate valve of claim 1 wherein said two closure plates each includes a circumferential edge and said closure plates are axially movable relative one to another in response to the pressure medium therebetween, a compensator extends along said outer circumferential edge of the two closure plates to form a space therebetween, said compensator being sealed to said closure plates to seal said space therebetween in a fluid-tight enclosure.
8. The parallel slide gate valve apparatus of claim 7 wherein said compensator includes a substantially tubular portion extending over the circumferential side edges of said closure plates and said tubular portion includes a corrugated configuration of at least a one half-shaft configuration extending between said closure plates, said substantially tubular portion being sealed in a fluid-tight manner along both circumferential side edges to said closure plates, a pressure medium pipe, said tubular portion having an opening in a sealing means sealing said pressure medium pipe within said corrugated configuration of said tubular opening for pressurizing of the space between said two closure plates.
9. The parallel slide gate valve of claim 8 wherein said substantially tubular portion includes first and second side edges respectively engaging said circumferential side edges of said closure plates, and said sealing means includes continuous welds connecting each side edge to the engaged plate and sealing the tubular portion to the plate.
10. The parallel slide gate valve apparatus of Claim 1 wherein said seal portions of said two closure plates include an enclosed annular space, a pressure medium connector connected to said annual space for introduction of a pressure medium into said annular space, said seal portions of said two closure plates bulging axially outwardly in response to a selected closure pressure within the said space.
11. The parallel slide gate valve apparatus of claim 1 including a guide tube connected to said closure plates and having end seal rings aligned with the seal portions of said closure plates, said guide tube having a pressure medium space between said seal rings and coupled to form a part of the pressure medium space associated with the seal portions of said two closure plates, said seal rings being configured to be pressed outwardly in response to a pressure medium introduced between said closure plates for sealing of said seal rings against the sealing surfaces of the nozzles.
12. The parallel slide gate valve apparatus of claim 11 wherein said two closure plates of said slide and said two seal rings of said guide tube are respectively integrally connected to said closure plates in a fluid-tight manner to seal said space.
13. The parallel slide gate valve apparatus of claim 11 including an outer casing including an enclosing box mounted within said casing, said enclosure plates forming opposite aligned side walls of said enclosing box, said seal rings forming an encircling side wall of said enclosing box and being connected to said aligned side walls to define a fluid-tight enclosure, said box having corner and edges rounded to correspond to the contour of the seal portions and of the seal rings.
14. The parallel slide gate valve apparatus of claim 7 wherein said casing includes an inlet nozzle side, said closure plates have aligned seal portions, and said space includes a connection to the inlet nozzle side of said casing to apply said inlet pressure to said seal portions.
15. The parallel slide gate valve apparatus of claim 1 including a first pipe connected to one of said nozzles of said slide, a non-return valve in said first pipe, said non-return valve opens only in the direction of the operating medium entering between said closure plates into the slide, a common pipe and a two-way valve connecting said first pipe to one of said nozzles and to said common pipe.
16. The parallel slide gate valve apparatus of Claim 1 wherein said seal portion of said closure plates include substantially flat surfaces, a seal ring interposed between the sealing surfaces of said closure plates and said casing said having groove-like recesses configured to receive said seal ring, a multi-layer resilient elastic diaphragm disposed within said groove-like recess, and a means coupled to said elastic diaphragm for moving of said elastic diaphragm for moving of said elastic diaphragm and the interrelated seal ring for loading of the diaphragm and moving of the ring into sealing engagement.
17. The parallel slide gate valve apparatus of Claim 16 wherein said diaphragm has inner and outer side edges, a sealing connector connecting said edges to said slide in a fluid-tight connection throughout the inner and outer edges, and thereby defining a fluid-tight chamber between said diaphragm and the slide, and a pressure medium pipe adapted to be connected to a pressure medium source connected to said chamber between said diaphragm and said slide.
18. The parallel slide gate valve apparatus of claim 16 including surrounding shafts located within said groove-like recess.
19. The parallel slide gate valve apparatus of claim 18 including a slide and wherein said diaphragm is spaced from the slide and within said groove-like recess, said last named spacing defining a pressure medium space extending around at least a portion of the seal ring.
20. The parallel slide gate valve apparatus of Claim 18 wherein said slide has an annular surface aligned with the diaphragm and has a radial cross-section and contour corresponding substantially to that of the diaphragm.
21. The parallel slide gate valve apparatus of Claim 20 in that surrounding recess included by said diaphragm is extended from a corresponding surrounding recess of the associated annular space of the slide in the direction of movement of the seal ring.
22. The parallel slide gate valve apparatus of Claim 21 wherein said diaphragm includes a plurality of strips of material resistant to high temperature, said strips being in close contact with each other over their entire length and width in the absence of pressure in said pressure medium space.
23. The parallel slide gate valve apparatus of Claim 22 including a pressure medium storage unit includes an expandable container connected to said pressure medium space and includes a constant load unit creating an initial constant tension load from said pressure medium space.
24. The parallel slide gate valve apparatus of Claim 23 wherein said constant load unit is coupled to a drive of the slide and is operable to relieve the load on the pressure medium storage container in response to operation of the drive of the slide.
25. The parallel slide gate valve apparatus of Claim 21 wherein said pressure medium loading is a gaseous material.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP4414176.9 | 1994-04-22 | ||
| DE4414176A DE4414176A1 (en) | 1994-04-22 | 1994-04-22 | Knife gate valve |
| PCT/EP1995/001488 WO1995029356A1 (en) | 1994-04-22 | 1995-04-20 | Gate valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2165687C true CA2165687C (en) | 1999-11-09 |
Family
ID=6516227
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002165687A Expired - Fee Related CA2165687C (en) | 1994-04-22 | 1995-04-20 | Parallel slide gate valve |
Country Status (11)
| Country | Link |
|---|---|
| EP (1) | EP0705402B1 (en) |
| JP (1) | JPH09501762A (en) |
| KR (1) | KR100366400B1 (en) |
| CN (1) | CN1057822C (en) |
| AT (1) | ATE204965T1 (en) |
| BR (1) | BR9506213A (en) |
| CA (1) | CA2165687C (en) |
| DE (2) | DE4414176A1 (en) |
| ES (1) | ES2163510T3 (en) |
| RU (1) | RU2151939C1 (en) |
| WO (1) | WO1995029356A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2018057692A1 (en) * | 2016-09-21 | 2018-03-29 | Dayco Ip Holdings, Llc | Valve gate within a venturi gap of a venturi device for producing vacuum |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19653456A1 (en) * | 1996-12-20 | 1998-07-09 | Zosel Dietrich Dipl Ing | poetry |
| US6215897B1 (en) | 1998-05-20 | 2001-04-10 | Applied Komatsu Technology, Inc. | Automated substrate processing system |
| US6079693A (en) * | 1998-05-20 | 2000-06-27 | Applied Komatsu Technology, Inc. | Isolation valves |
| JP2006526125A (en) | 2003-05-13 | 2006-11-16 | アプライド マテリアルズ インコーポレイテッド | Method and apparatus for sealing an opening in a processing chamber |
| KR100801230B1 (en) * | 2006-03-30 | 2008-02-11 | (주)현우산업 | Slide piping gate valve |
| KR101762986B1 (en) * | 2010-01-25 | 2017-07-28 | 배트 홀딩 아게 | Vacuum valve |
| EP3922888A1 (en) | 2013-05-31 | 2021-12-15 | Dayco IP Holdings, LLC | Sprung gate valves movable by an actuator |
| US9574677B2 (en) | 2013-05-31 | 2017-02-21 | Dayco Ip Holdings, Llc | Solenoid-powered gate valve |
| CN103322230B (en) * | 2013-06-30 | 2015-12-23 | 金川集团股份有限公司 | pipeline valve |
| JP6571083B2 (en) * | 2013-08-30 | 2019-09-04 | デイコ アイピー ホールディングス, エルエルシーDayco Ip Holdings, Llc | Spring loaded gate valve movable by solenoid actuator |
| BR112016010714A2 (en) | 2013-11-12 | 2017-09-12 | Dayco Ip Holdings Llc | diesel engine fluid cooling system having a solenoid actuated gate valve |
| US10221867B2 (en) | 2013-12-10 | 2019-03-05 | Dayco Ip Holdings, Llc | Flow control for aspirators producing vacuum using the venturi effect |
| EP3094900B1 (en) | 2013-12-11 | 2020-09-16 | Dayco IP Holdings, LLC | Magnetically actuated shut-off valve |
| CN104763818B (en) * | 2015-03-24 | 2017-03-29 | 苏州菱欧自动化设备有限公司 | A kind of switch valve |
| US9599246B2 (en) | 2015-08-05 | 2017-03-21 | Dayco Ip Holdings, Llc | Magnetically actuated shut-off valve |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE720599C (en) * | 1939-11-11 | 1942-05-09 | H A Brassert & Co | Knife gate valve for shutting off gas lines |
| DE1189345B (en) * | 1960-07-18 | 1965-03-18 | Hermann Rappold & Co G M B H | Gate valves, especially hot wind valves with cooling |
| DE1900538C3 (en) * | 1969-01-07 | 1980-02-07 | Exxon Research And Engineering Co., Linden, N.J. (V.St.A.) | Gate valve for large pipe diameters |
| US3596874A (en) * | 1969-06-20 | 1971-08-03 | American Smelting Refining | Shutoff dampers |
| US3684239A (en) * | 1970-11-30 | 1972-08-15 | Rockwell Mfg Co | Butterfly type valve with stress seal |
| CH675286A5 (en) * | 1988-02-04 | 1990-09-14 | Sulzer Ag | |
| DE4011274C1 (en) * | 1990-04-06 | 1991-08-01 | Zimmermann & Jansen Gmbh, 5160 Dueren, De |
-
1994
- 1994-04-22 DE DE4414176A patent/DE4414176A1/en active Pending
-
1995
- 1995-04-20 AT AT95917942T patent/ATE204965T1/en not_active IP Right Cessation
- 1995-04-20 CN CN95190456A patent/CN1057822C/en not_active Expired - Fee Related
- 1995-04-20 ES ES95917942T patent/ES2163510T3/en not_active Expired - Lifetime
- 1995-04-20 EP EP95917942A patent/EP0705402B1/en not_active Expired - Lifetime
- 1995-04-20 WO PCT/EP1995/001488 patent/WO1995029356A1/en active IP Right Grant
- 1995-04-20 RU RU96100747/06A patent/RU2151939C1/en not_active IP Right Cessation
- 1995-04-20 CA CA002165687A patent/CA2165687C/en not_active Expired - Fee Related
- 1995-04-20 KR KR1019950705836A patent/KR100366400B1/en not_active IP Right Cessation
- 1995-04-20 BR BR9506213A patent/BR9506213A/en not_active IP Right Cessation
- 1995-04-20 DE DE59509554T patent/DE59509554D1/en not_active Expired - Fee Related
- 1995-04-20 JP JP7527348A patent/JPH09501762A/en not_active Ceased
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2018057692A1 (en) * | 2016-09-21 | 2018-03-29 | Dayco Ip Holdings, Llc | Valve gate within a venturi gap of a venturi device for producing vacuum |
| CN109715998A (en) * | 2016-09-21 | 2019-05-03 | 戴科知识产权控股有限责任公司 | Gate valve in the venturi gap of Venturi for generating vacuum |
Also Published As
| Publication number | Publication date |
|---|---|
| KR960703217A (en) | 1996-06-19 |
| WO1995029356A1 (en) | 1995-11-02 |
| BR9506213A (en) | 1997-09-30 |
| CN1129029A (en) | 1996-08-14 |
| JPH09501762A (en) | 1997-02-18 |
| EP0705402A1 (en) | 1996-04-10 |
| CN1057822C (en) | 2000-10-25 |
| KR100366400B1 (en) | 2003-03-29 |
| ES2163510T3 (en) | 2002-02-01 |
| DE4414176A1 (en) | 1995-10-26 |
| ATE204965T1 (en) | 2001-09-15 |
| DE59509554D1 (en) | 2001-10-04 |
| EP0705402B1 (en) | 2001-08-29 |
| RU2151939C1 (en) | 2000-06-27 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |