WO1995001526A1 - Joint de tige rotative d'une vanne - Google Patents

Joint de tige rotative d'une vanne Download PDF

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Publication number
WO1995001526A1
WO1995001526A1 PCT/US1994/007332 US9407332W WO9501526A1 WO 1995001526 A1 WO1995001526 A1 WO 1995001526A1 US 9407332 W US9407332 W US 9407332W WO 9501526 A1 WO9501526 A1 WO 9501526A1
Authority
WO
WIPO (PCT)
Prior art keywords
bellows
shaft
seal
valve according
housing
Prior art date
Application number
PCT/US1994/007332
Other languages
English (en)
Inventor
Antonius Adrianus Maria Voermans
Original Assignee
Keystone International Holdings Corp.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Keystone International Holdings Corp. filed Critical Keystone International Holdings Corp.
Priority to EP94922048A priority Critical patent/EP0706623A1/fr
Priority to AU72526/94A priority patent/AU7252694A/en
Publication of WO1995001526A1 publication Critical patent/WO1995001526A1/fr

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Classifications

    • 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
    • F16K41/00—Spindle sealings
    • F16K41/003—Spindle sealings by fluid
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • F16J15/43—Sealings between relatively-moving surfaces by means of fluid kept in sealing position by magnetic force
    • 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
    • F16K41/00—Spindle sealings
    • F16K41/10—Spindle sealings with diaphragm, e.g. shaped as bellows or tube

Definitions

  • the invention relates to a valve for reservoirs and pipes, comprising a housing, a shut-off element, a rotatable operating shaft which runs through the housing, and a primary seal on the shaft.
  • valves for regulating the system and the reservoir.
  • These valves are, for example, butterfly valves, plug valves and ball valves.
  • the operating shaft which extends outwards through the housing has to be rotated by hand or otherwise over an angle of 90° . A rotation of 180° is also possible, however.
  • a primary seal is arranged on the shaft.
  • a disadvantage of this known valve is that when in use, sooner or later the primary seal can start leaking. In pipe systems and reservoirs for dangerous substances this is exceedingly undesirable.
  • the valve according to the invention comprises in the first of its coordinate embodiments the measure that the valve comprises a secondary seal, which, as seen from the shut-off element, is placed beyond the primary seal about the shaft and comprises a bellows substantially manufactured from a flexible material, one end of the bellows being attached to the shaft and the other end to the housing, the bellows permitting the shaft to rotate along a part of a revolution, and with that twists, and a coiled spring being arranged on the side of the bellows which is turned away from the space which connects to the primary seal, which coiled spring supports the bellows, which coiled spring is manufactured from a substantially circular thread, and which is at least as long as the twisting portion of the bellows, and which coiled spring is attached with one end of the shaft and with the other end to the housing in order to obtain a torsion which substantially corresponds to that of the bellows.
  • This coiled spring is manufactured from substantially round wire, so that in the case of high pressure of the leaked fluid the coiled spring will not cut into the flexible material. Because of its shape the coiled spring is automatically so rigid, that it does not have to be supported against the shaft or the housing. Because the coiled spring, just as the housing, is attached with one end to the shaft and with the other end to the bellows, and is at least equally long as the twisting portion of the bellows, at most only some displacement will take place between the bellows and the coiled spring when the shaft is rotated. As far as the secondary seal is concerned the required moment for rotating the operating shaft is thus kept as low as possible and is in effect limited to the moment that is required for twisting the bellows and the spring.
  • the valve according to the invention comprises the measure, that the valve comprises a secondary seal, which, as seen from the shut-off element, is placed beyond the primary seal about the shaft and comprises a bellows substantially manufactured from a flexible material, one end of the bellows being attached to the shaft and the other end to the housing, the bellows permitting the shaft to rotate along a part of a revolution, and with that twists, the flexible material of the bellows incorporating a coiled spring, supporting the bellows, the windings of which rest free from one another, and which is equally long as the twisting portion of the bellows.
  • the coiled spring is incorporated in the flexible material of the bellows. To ensure that the bellows forms a unit, the windings of the coiled spring rest separate from one another.
  • the operation of this embodiment of the secondary seal is the same as that of the above embodiment.
  • the valve according to the invention comprises the measure, that the valve comprises a secondary seal, which, as seen from the shut-off element, is placed beyond the primary seal about the shaft and comprises a bellows substantially manufactured from a flexible material, one end of the bellows being attached to the shaft and the other end to the housing, the bellows permitting the shaft to rotate along a part of a revolution, and with that twists, and a synthetic having a very low friction coefficient being arranged on the bellows on the side of the bellows which is turned away from the space that connects to the primary seal, allowing support of the bellows against either the shaft, or the housing.
  • the synthetic with a low friction coefficient is arranged which will indeed be supported against the shaft or the housing when the leaked fluid applies pressure to the bellows.
  • the surface of the bellows is herewith equally loaded.
  • the bellows has its released state between the opened and closed position of the shut-off element, preferably halfway through the total angle of rotation of the operating shaft. In this way only in the extreme positions of the shut-off element does the required moment for the twisting of the bellows reach its maximum value, which is lower than when the released state of the bellows is at a different angle of rotation of the operating shaft.
  • the total angle of rotation of the operating shaft is approximately 90° .
  • the coiled spring advantageously has at least approximately 10-12 windings along the twisting portion of the bellows, at a total angle of rotation of the operating shaft of approximately 90° and the released state of the bellows halfway through the total angle of rotation.
  • the flexible material of the bellows can accommodate this slight shifting in the area between the adjoining windings, as a result of which the bellows does not have to shift over a portion of the windings.
  • the required moment for rotating the operating shaft is thus minimized and limited to the torsion of the bellows and the spring itself. Neither will any wear of the bellows occur.
  • the bellows is advantageously circularly cylindrical so that the load on it is symmetrical.
  • the bellows is substantially manufactured from rubber, from a synthetic, preferably a fluor polymer, or from a laminate of synthetics and/or rubbers.
  • the material depends on the fluid which is sealed.
  • the end of the bellows which is to be attached to the shaft is of metal, to which the flexible part of the bellows is attached, and the metal end and the shaft being statically sealed in relation to each other, for example with the help of 0-rings.
  • the bellows can easily be attached to the 30 shaft.
  • the other end of the bellows is also made of metal.
  • the metal end is advantageously attached to either the shaft or the housing by means of a pin. Because of this the bellows is easily detachable.
  • the flexible end of the bellows is advantageously attached to either the shaft or the housing by clamping. In this way a simple, leakproof retaining of the flexible end of the bellows is obtained. It is then of advantage that the flexible end of the bellows is provided with a metal ring. Then the end cannot be pulled out of the retaining.
  • the flexible end of the bellows can also advantageously be attached to either the housing or to the shaft by vulcanizing. Consequently, a hermetically closed, static seal is formed. In the case of such an attachment free of pressure the chance of crack formation in the rubber is reduced.
  • the secondary seal also advantageously comprises a magnetic fluid seal, which, as seen from the shut-off element, is arranged beyond the bellows about the shaft.
  • the flexible bellows will indeed stem liquids but will always be slightly permeable for vapors or gases. In order to prevent vapors or gases from leaking into the surroundings, the magnetic fluid seal is placed.
  • the magnetic fluid seal comprises at least one magnet, magnetic liquid, a magnetic conducting component, and two pole pieces on both sides of the magnet, the magnet, the pole pieces, the magnetic liquid and the component forming a magnetic circuit.
  • the magnetic conducting component is the shaft itself, the shaft is round, and the magnet and the pole pieces are arranged annularly about the shaft, the pole pieces comprising various annular ridges, which are at a short distance from the shaft, and the magnetic fluid spanning the distance between the ridges and the shaft.
  • a radial magnetic fluid seal is formed, in which the magnetic fluid between the shaft and the groove can always span a certain difference in pressure, proportional to the quantity of magnetizable particles in the fluid, as a result of which, depending on the number of ridges, the total pressure difference between the passed through gas or the passed-through vapor and the surroundings is spanned, so that no measurable quantity of passed through gas or vapor will make its way into the surroundings at all.
  • the radial magnetic fluid seal has the advantages that no wear occurs, that no additional moment is needed when rotating the operating shaft, and that the seal can be small. To obtain an optimum seal the slot between the ridges and the shaft has to be small, so that the shaft has to be positioned accurately.
  • the magnetic fluid seal advantageously contains a magnetic fluid with a very high concentration of magnetizable particles, as a result of which the pressure difference which can be spanned per ridge increases.
  • Highly magnetizable fluids display a very viscous behavior, so that the application can only be used with slow moving shafts, such as in a valve, and not with high-speed shafts such as in pumps.
  • the magnetic fluid seal can also be executed as an axial magnetic fluid seal.
  • the magnet is disc-shaped, the pole pieces are disc-shaped and placed at a radially different distance from the shaft, and the magnetic conducting component is a disc, which is arranged opposite the pole pieces, the pole pieces comprising annular ridges at a short distance from the disc, the magnetic fluid being arranged between the pole pieces and the disc, and either the magnet or the disc being connected to the shaft, and the other being connected to the housing.
  • An advantage of this embodiment is that the magnet and the disc can easily be positioned at a short distance from each another. Just as with the radial magnetic fluid seal no wear occurs. As the build-up of pressure in an axial direction has to be compensated, the components have to be made heavier to avoid bending and the axial seal will be larger than the radial seal.
  • a spring element is advantageously arranged near the axial magnetic fluid seal, which presses the magnet with pole pieces and the disc against each another, inducing a zero slot. Consequently, a very high tightness of the magnetic fluid seal arises. Attendant effects such as an additional moment and wear will be small due to the lubricating effect of the magnetic fluid.
  • a conventional dynamic seal has been incorporated in the grooves between the ridges and/or between the pole pieces.
  • the conventional dynamic seal such as an O-ring or another sort of packing, is lubricated by the magnetic fluid so friction ancl wear will hardly occur.
  • the pressure tightness of the seal is enhanced by this measure.
  • a fireproof shut-off ring is also advantageously arranged, which is arranged about the shaft, and which is manufactured from a memory metal, the ring, when in a cold state having been given a shape in which the shaft is free-running, and which in the case of fire adopts a shape such that it closes against the shaft and the housing.
  • a fireproof seal of that sort is also arranged in front of the secondary seal. In this way it is ensured that after a fire the secondary seal with the leaked fluid can easily be replaced.
  • the fireproof seal preferably changes its shape at a temperature which is lower than the critical temperature where the secondary seal fails, for example 120-170° .
  • the ring advantageously has a one-way shape memory and does not return to the shape of its cold state when it cools after heating. After the fire the leaked-out fluid is then retained in the housing of the secondary seal.
  • a monitoring system is advantageously arranged, which gauges the pressures which occur in front of and beyond each part of the secondary seal, to determine the occurrence and the rate of leakage in order to carry out maintenance. So it is ensured that maintenance can be carried out when the leakage has reached a certain level or when the secondary seal or a part thereof fails.
  • the monitoring system advantageously comprises pressure gauges, and a membrane is arranged in the housing near the bellows to control the operation of the bellows. The membrane is arranged between the space which connects to the primary seal and a pressure gauge and is made of the same flexible material as the bellows.
  • the extent of leakage of the seals can be determined.
  • the membrane has been added to check whether the bellows is still intact.
  • the pressures beyond the bellows and beyond the membrane are equal in the case of a functioning bellows. If the bellows has failed, then the pressure beyond the bellows is higher than the pressure beyond the membrane.
  • the pressures are advantageously gauged ahead of and between the pole pieces, thus determining the carrying out of maintenance or not and the possible occurrence of leakage. If the pressure between the pole pieces is zero, in other words equal to the ambient pressure, then no leakage will occur into the surroundings. If this pressure is larger than zero then the escaped fluid has to be discharged, the possibility of leakage to the surroundings being present. If the pressure ahead of the pole piece goes above a certain value, then the leaked fluid should be discharged to prevent leakage of the magnetic fluid seal starting.
  • the pressure between the secondary seal and the conventional seal is advantageously gauged. If this pressure is higher than zero, then maintenance should be carried out immediately because leakage will take place into the surroundings.
  • the conventional seal limits the extent of the leakage.
  • the bellows, the magnetic fluid and the fireproof shut-off ring can also be used separately for sealing the shaft of a valve.
  • Fig. 1 is a simplified representation of the valve according to the invention.
  • Fig. 2 to 7 show various embodiments of the bellows seal according to the invention, which is a part of the valve according to fig. 1.
  • Figs. 8 and 9 show various embodiments of a magnetic fluid seal, which is a part of the valve according to fig. 1.
  • Figs. 10 and 11 show fireproof seals in a cold and heated state, as these can be incorporated in the valve according to fig. 1.
  • Fig. 1 shows that the valve according to the invention is incorporated in a pipe 1, and comprises a housing 2, the lowest portion 2 A of which is placed in the pipe 1, and in which a rotatable shut-off element 3 is arranged.
  • the shut-off element 3 is rotated with an operating shaft 4, which with the help of a primary seal 5 seals the fluid present in the pipe 1 vis-a-vis the surroundings.
  • the fluid can be a chemical, liquid, gas, vapor or liquefied material. It will be understood that instead of being incorporated in a pipe, the valve can be connected to a reservoir.
  • a portion of the housing 2B is placed, in which the bellows seal 6 is incorporated.
  • a portion of the housing 2C is placed, in which the magnetic fluid seal 7 is incorporated.
  • the bellows seal 6 and the magnetic fluid seal 7 together form the secondary seal.
  • fireproof shut-off rings 8 and 9 are arranged.
  • a conventional seal 10 is arranged. All the seals are placed about the operating shaft 4.
  • a monitoring system gauges the pressure, ahead of, beyond and in-between the components of the secondary seal.
  • a membrane 11 is arranged, behind which a pressure gauge M2 is placed.
  • the figures 2 to 7 show different embodiments of the bellows seal 6 as shown in fig. 1.
  • Fig. 2 shows the bellows seal 6A, the bellows 12 being 10 completely made of flexible material and the pressure of the fluid that has leaked along the primary seal 5 will be exerted on the outer side of the bellows.
  • a coiled spring 13 is arranged between the bellows 12 and the operating shaft 4 which runs along the whole length of the bellows.
  • a bush 19 one side of the bellows is clamped to a flange 16 welded to the shaft and the other side of the bellows is clamped to the housing 2B with the help of a flange 17. Locking against loosening of the bellows is ensured with the help of annular cams 18 attached to the flanges 16 and 17.
  • Locking between flange 16 and shaft 4 and flange 17 and housing 2B, respectively, can be guaranteed by fixing means yet to be specified more closely.
  • the outer ends of the coiled spring 13 are incorporated near the flange 16 in the shaft 4 and near the flange 17 in this flange.
  • a similar conventional seal 24 can be incorporated into the flange 17 if no use is made of a magnetic fluid seal 7.
  • Fig. 3 shows a second embodiment 6B of the bellow seal 6.
  • the outer end 20 of the bellows to be attached to the shaft is of metal, and this metal outer end is attached to the shaft 4 with the help of a pin 21. Sealing of the metal outer end onto the shaft is obtained by conventional static seals 22.
  • the coiled spring 13 only runs along the flexible portion of the bellows. Otherwise this embodiment is the same as that of fig. 2.
  • Fig. 4 shows an embodiment 6C of the bellow seal 6 with a metal outer end 20 of the bellows, which is welded to the shaft 4.
  • Attaching the flexible portion of the bellows to the housing 2B takes place here by vulcanizing the flexible portion of the bellows to the housing.
  • the flexible portion of the bellows has to made substantially of rubber.
  • Attaching the flexible portion of the bellows to the metal outer end 20 can also take place by vulcanization.
  • the coiled spring 13 is incorporated in the seal in a manner analogous to that of fig. 3.
  • Fig. 5 shows an embodiment 6D of the bellows seal 6, in which the coiled spring 13 is incorporated in the flexible portion of the bellows 12. Otherwise this embodiment is the same as that of fig. 4.
  • Fig. 6 shows an embodiment 6E of the bellows seal 6 in which instead of a coiled spring a synthetic 26 with a very low friction coefficient is arranged between the flexible portion of the bellows 12 and the shaft. A lubricating fluid 27 is applied between the synthetic 26 and the flexible portion of the bellows. Otherwise this embodiment is the same as that of fig. 5.
  • Fig. 7 shows an embodiment 6F of the bellows seal 6, in which the bellows does not have a metal outer end, but the flexible outer ends of the bellows 12 are provided with metal rings 28 and 29.
  • a synthetic 26 with a very low friction coefficient is applied between the bellows 12 and the shaft 4.
  • Fig. 8 shows a radial magnetic fluid seal 7 with a permanent magnet 30, two pole pieces 32 and 33 with several annular ridges 34 placed at a short distance from the shaft 4. Between the pole pieces and the shaft 4 a magnetic fluid 31 is applied, as a result of which there is a closed magnetic circuit.
  • the magnetic fluid 31 consists of a fluid in which magnetizable particles are incorporated.
  • a conventional dynamic seal such as an O-ring 41 or a packing 42 of a different kind can be arranged between the ridges of the pole pieces or between the pole pieces themselves.
  • Fig. 9 shows an axial magnetic fluid seal.
  • the permanent magnet 35 is annular and arranged on the shaft.
  • the pole pieces 36 and 37 are disc-shaped and arranged at different distances from the shaft on the permanent magnet 35, at a short distance from a disc 38, which is attached to the housing 2C.
  • the pole pieces 36 and 37 have annular ridges 39, and the magnetic fluid 31 is applied between the pole pieces and the disc 38. In this way a magnetic circuit is formed which does not run through the shaft.
  • a spring element 40 the disc 38 can be pressed against the ridges 39 of the pole pieces 36 and 37, as a result of which a very strong magnetic field is formed.
  • conventional dynamic seals such as an O-ring 41 or a packing 42 of a different kind can be arranged between the ridges 39 of the pole pieces 36 or 37 or between the pole pieces .
  • Fig. 10 shows a fireproof seal ring 8/9, the left side of the figure representing the ring in a cold state and the right side of the figure representing the ring in a heated state.
  • the ring is made of a material with a one-way shape memory, as a result of which in the case of fire the ring takes on the shape according to the right side of fig. 10 above the critical temperature of the secondary seal, for example 120- 170 °C. Due to this change in shape the ring clamps around the shaft 4 and in the housing 2, so that a complete shut-off is obtained.
  • the ring Upon cooling after the fire the ring retains the shape which it took on in the heated state.
  • FIG 11 shows another embodiment of the fireproof seal ring.
  • This ring was originally a conical one (at the right in the figure) which has been made cylindrical by butting the lower, wide portion and stretching the upper, narrow portion.
  • the lattice structure here is such that upon heating the ring passes from the shape, on the left in the figure, to the original conical shape on the right in the figure and then a complete seal is provided.
  • the parts of the housing 2A, 2B and 2C are sealed vis-a-vis one another by fireproof static seals. This is not shown.
  • the bellows seal will have to stem this leakage, while the operating shaft 4 should still be operable with small moment. For that reason the coiled spring or the synthetic with a low friction coefficient is arranged in the bellows seal on the inner side of the bellows or a coiled spring is incorporated in the bellows, as a consequence of which the additional moment, even under high pressure, is mainly determined by the torsion of the flexible portion of the bellows.
  • the bellows seals off against fluids, but is not entirely hermetic for vapors or gasses, because diffusion through the material can occur. In order to stop this diffusion leakage of the flexible bellows the magnetic fluid seal 7 is put into place.
  • the magnetic fluid at every ridge can stem a pressure difference of approximately 0,5 bar.
  • the magnetic fluid is pushed aside and gas or vapor will pass, but when the difference in pressure again gets lower than 0,5 bar the magnetic fluid will automatically restore the seal at the ridge.
  • the magnetic fluid seal will stem the vapors or gases entirely, a leakage of less than 10-9mbarl/s as a consequence of diffusion of the vapors or gases through the magnetic fluid being feasible.
  • a conventional dynamic shaft seal is included between, for example, the first and the second ridge, as seen from the bellows seal.
  • a conventional dynamic seal 10 is included in the housing beyond the magnetic fluid seal.
  • fireproof sealing rings 8 and 9 are arranged about the shaft, since in the event of fire the bellows seal 6 and the magnetic fluid seal 7 will fail. Under the higher temperature of the fire the fireproof sealing rings will, however, seal the valve hermetically, so that no fluid will leak into the surroundings.
  • the pressure gauges Ml to M5 are arranged so as to be able to gauge the pressure of the leaked fluid at the various places ahead of and behind the seals.
  • the gauged pressures at the various pressure gauges are named PI to P5, respectively. If the pressure P4 is higher than 0, then the magnetic fluid seal is leaking and there should be immediate intervention. If the pressure P5 is higher than 0, but the pressure P4 remains 0, there is a chance of leakage into the surroundings and maintenance should be carried out in due course. On the basis of pressure P3 it can be determined whether the pressure in front of the magnetic fluid seal is so high that controlled discharge of the leaked fluid has to take place.
  • the membrane 11 is arranged, the membrane being made of the same material as the flexible bellows and through which as much fluid diffuses as through the bellows 6.
  • the operation of the primary seal is determined on the basis of pressure PI.
  • the valve is designed for a lifespan in which the shut-off element can be opened and closed at least 50,000 times. Seeing as the primary seal could fail directly after having come into use, the bellows seal has to be able to resist the working pressure throughout its whole lifespan.
  • the embodiment of the bellows with the coiled spring is therefore advantageous, in that a sufficiently large number of windings, preferably a minimum of 10-12, run along the flexible material and that they have a circular cross section and rest next to each other, as a result of which the flexible material is not pressed between the windings and is not cut into, and as a consequence of which hardly any or no wear of the bellows and friction between the bellows and the coiled spring will occur when the operating shaft is rotated.
  • the space between the housing and the operating shaft with the seals should be as small as possible.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Abstract

L'invention concerne une vanne de conduit ou de réservoir composée d'un carter, d'un élément de fermeture, d'une tige rotative s'étendant à travers le carter et d'un joint primaire sur la tige. Vu depuis l'élément de fermeture, un joint secondaire est placé au-delà du joint primaire autour de la tige. Le joint secondaire est composé d'un joint d'étanchéité à soufflet et d'un joint d'étanchéité magnétique en avant et au-delà duquel est disposée une bague de fermeture ignifuge autour de l'arbre. Un dispositif de contrôle permet de détecter les fuites du conduit. Ce dispositif de contrôle permet de vérifier la présence d'une fuite vers l'extérieur, la nécessité de procéder à l'entretien, ainsi que l'intégrité totale ou partielle du joint.
PCT/US1994/007332 1993-07-02 1994-06-30 Joint de tige rotative d'une vanne WO1995001526A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP94922048A EP0706623A1 (fr) 1993-07-02 1994-06-30 Joint de tige rotative d'une vanne
AU72526/94A AU7252694A (en) 1993-07-02 1994-06-30 Seat for the rotating shaft of a valve

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL9301162A NL9301162A (nl) 1993-07-02 1993-07-02 Afdichting voor as van afsluiter.
NL9301162 1993-07-02

Publications (1)

Publication Number Publication Date
WO1995001526A1 true WO1995001526A1 (fr) 1995-01-12

Family

ID=19862612

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1994/007332 WO1995001526A1 (fr) 1993-07-02 1994-06-30 Joint de tige rotative d'une vanne

Country Status (4)

Country Link
EP (1) EP0706623A1 (fr)
AU (1) AU7252694A (fr)
NL (1) NL9301162A (fr)
WO (1) WO1995001526A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2228571A1 (fr) * 2009-03-12 2010-09-15 Ferrotec (UK), Ltd. Traversée pour arbre rotatif utilisant un fluide magnétique avec capacité de détection et de communication
JP2016098957A (ja) * 2014-11-25 2016-05-30 三菱重工業株式会社 弁ケーシング、これを備えた弁、弁を備えたタービン装置、および弁ケーシングの雰囲気ガス侵入防止方法
US11339876B2 (en) * 2020-01-24 2022-05-24 Ckd Corporation Butterfly valve

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB577699A (en) * 1944-06-22 1946-05-28 Saunders Valve Co Ltd Improvements in cocks
DE2015042A1 (de) * 1970-03-28 1971-10-21 Dynamit Nobel Ag Abdichtung einer verdrehbaren Welle
GB2039333A (en) * 1979-01-02 1980-08-06 Klein Schanzlin & Becker Ag Bellows-type sealing element
US4462422A (en) * 1982-03-11 1984-07-31 Kerotest Manufacturing Corp. Bellows sealed stem for rotary valve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB577699A (en) * 1944-06-22 1946-05-28 Saunders Valve Co Ltd Improvements in cocks
DE2015042A1 (de) * 1970-03-28 1971-10-21 Dynamit Nobel Ag Abdichtung einer verdrehbaren Welle
GB2039333A (en) * 1979-01-02 1980-08-06 Klein Schanzlin & Becker Ag Bellows-type sealing element
US4462422A (en) * 1982-03-11 1984-07-31 Kerotest Manufacturing Corp. Bellows sealed stem for rotary valve

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2228571A1 (fr) * 2009-03-12 2010-09-15 Ferrotec (UK), Ltd. Traversée pour arbre rotatif utilisant un fluide magnétique avec capacité de détection et de communication
JP2016098957A (ja) * 2014-11-25 2016-05-30 三菱重工業株式会社 弁ケーシング、これを備えた弁、弁を備えたタービン装置、および弁ケーシングの雰囲気ガス侵入防止方法
US11339876B2 (en) * 2020-01-24 2022-05-24 Ckd Corporation Butterfly valve

Also Published As

Publication number Publication date
AU7252694A (en) 1995-01-24
EP0706623A1 (fr) 1996-04-17
NL9301162A (nl) 1995-02-01

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