WO2024028020A1 - Soupape de réservoir, et procédé de fabrication d'une soupape de réservoir - Google Patents

Soupape de réservoir, et procédé de fabrication d'une soupape de réservoir Download PDF

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Publication number
WO2024028020A1
WO2024028020A1 PCT/EP2023/068374 EP2023068374W WO2024028020A1 WO 2024028020 A1 WO2024028020 A1 WO 2024028020A1 EP 2023068374 W EP2023068374 W EP 2023068374W WO 2024028020 A1 WO2024028020 A1 WO 2024028020A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing
tank
valve
sealing surface
conical
Prior art date
Application number
PCT/EP2023/068374
Other languages
German (de)
English (en)
Inventor
Marco Stieber
Jens-Peter Nagel
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2024028020A1 publication Critical patent/WO2024028020A1/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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
    • F16J15/108—Special methods for making a non-metallic packing
    • 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
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
    • F16J15/102—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing characterised by material
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/30—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces specially adapted for pressure containers
    • F16K1/301—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces specially adapted for pressure containers only shut-off valves, i.e. valves without additional means
    • F16K1/303—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces specially adapted for pressure containers only shut-off valves, i.e. valves without additional means with a valve member, e.g. stem or shaft, passing through the seat
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • F16K1/38—Valve members of conical shape
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/44—Details of seats or valve members of double-seat valves
    • F16K1/443—Details of seats or valve members of double-seat valves the seats being in series
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/46—Attachment of sealing rings
    • F16K1/465—Attachment of sealing rings to the valve seats
    • 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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems
    • F16K15/063—Check valves with guided rigid valve members with guided stems the valve being loaded by a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C13/00—Details of vessels or of the filling or discharging of vessels
    • F17C13/04—Arrangement or mounting of valves

Definitions

  • the invention relates to a tank valve for a pressure tank, in which a compressed gas is stored, with an internal tank pressure varying between a high pressure value and a low pressure value depending on a filling state, with a guide body and with a valve piston biased into a closed position by a closing spring which is guided to be movable back and forth in a guide recess of the guide body between the closed position and an open position, a conical sealing seat of the tank valve comprising a first conical sealing surface and a second conical sealing surface, which come into sealing contact with one another when the valve piston assumes its closed position .
  • Common sealing methods here are adhesive or welded connections as non-removable seals.
  • elastomer seals such as O-rings in combination with support rings, are usually used.
  • the gas must not be released uncontrollably in a workshop.
  • One method here is to let the gas, such as hydrogen, escape into the open air, which means it is lost. This can be done, for example, via a normal removal path, which can take a lot of time depending on the filling quantity due to the respective throttle cross sections.
  • An alternative to this is to loosen a screw plug, which allows the gas to suddenly escape from the pressure tank. Such rapid venting of the pressure tank can usually only be achieved with a very complex device.
  • Standard vent valves for hydrogen applications include, among other things, elastomer or other plastic seals, which can wear due to relative movement, for example to metal components. Examples of this are moving radial seals in bores, such as O-rings, support rings or the like, or abrasion in cone seals due to relative rotation of the sealing partners.
  • the slightest damage to the seals which are usually “FKM” or “EPDM” in hydrogen applications, can lead to a leak in the tank system. This can mean that the tank empties itself after weeks or even a few days. In the worst case, this results in the escaped hydrogen mixing with the oxygen from the ambient air in an enclosed space, for example the interior of a motor vehicle or a garage, to form an explosive gas.
  • Conventional ventilation valves therefore often cannot be used multiple times and must be fitted with new seals after use for the above reasons.
  • the object of the invention is to improve a tank valve according to the preamble of claim 1 with regard to good sealing of the conical sealing seat during operation at widely varying pressures.
  • the object is achieved in a tank valve according to the preamble of claim 1 in that at least one of the sealing surfaces comprises at least two annular sealing sections which, depending on the internal tank pressure acting on the valve piston in the same direction as the biasing force of the closing spring, come into contact with the other conical sealing surface.
  • the compressed gas is preferably hydrogen.
  • the pressure tank is preferably a hydrogen tank in which hydrogen is stored, which is used as fuel in a fuel cell system. Another application, for example, is hydrogen direct injection.
  • the tank valve is, for example, a tank ventilation valve or a tank drain valve.
  • the conical sealing seat advantageously comprises an inner cone and an outer cone.
  • the conical sealing surfaces preferably each have the shape of a truncated cone shell.
  • a preferred embodiment of the tank valve is characterized in that the annular sealing sections are formed from different materials.
  • the different materials preferably include a metal and a plastic.
  • the metal is, for example, steel.
  • the plastic is, for example, a polyimide.
  • the plastic material can also be an elastomer, for example.
  • the metal, especially steel offers the advantage that high forces can be transmitted.
  • the plastic material takes on the sealing function in the sealing section equipped with it, preferably at low pressures. At high pressures, the sealing is achieved with the aid of a supporting function performed by the metal, in particular the steel. This support function becomes an irreversible one Deformation of the plastic material prevented In the plastic material from which the annular sealing section for the low pressures is formed, a reversible deformation is advantageously permitted to represent the sealing function.
  • a further preferred embodiment of the tank valve is characterized in that the two conical sealing surfaces have cone angles with an angular difference, which results in a sealing gap between the conical sealing surfaces, which expands radially inwards starting from a circular contact area. As the pressure inside the tank increases, this sealing gap decreases until it approaches zero.
  • the angular difference is preferably only a few degrees.
  • a further preferred embodiment of the tank valve is characterized in that the first conical sealing surface has an outer diameter that is smaller than an additional outer diameter of an outer annular sealing section of the second conical sealing surface. This makes it possible to easily display the previously described circular contact area between an outer edge of the first conical sealing surface and the outer annular sealing section of the second conical sealing surface.
  • a further preferred embodiment of the tank valve is characterized in that an additional inner diameter between the outer annular sealing section and an inner annular sealing section of the second conical sealing surface is larger than an inner diameter of the first conical sealing surface.
  • a further preferred embodiment of the tank valve is characterized in that the inner diameter of the first conical sealing surface is larger than a main inner diameter of the second conical sealing surface.
  • a further preferred embodiment of the tank valve is characterized in that the first conical sealing surface is formed on the valve piston, with the second conical sealing surface being formed on the guide body.
  • the valve piston and the guide body are both preferably made of a metal, in particular steel.
  • On the guide body only the outer circular ring-like sealing section is advantageously formed from a non-metallic material, in particular from a plastic material. In this way, a large range of the internal tank pressure range can be easily covered during operation of the pressure tank with a highly effective sealing function.
  • the above-mentioned task is alternatively or additionally achieved in that a sealing body is pressed into an annular groove provided on the guide body or the valve piston before final processing in order to represent one of the two annular sealing sections, whereby the Annular groove and the sealing body are designed so that the sealing body protrudes from the annular groove with a projection to be processed.
  • the annular groove is preferably provided in the second conical sealing surface on the guide body.
  • the sealing body is preferably designed as a sealing ring. In its raw state, the sealing ring has a substantially rectangular cross section. Only during final processing is the outer circular ring-like sealing section created on the sealing ring. In this way, a desired surface quality of the outer annular sealing section is made possible in a simple manner.
  • a preferred exemplary embodiment of the method is characterized in that the sealing body is machined in a clamping with a guide diameter on the inside of the guide body or outside of the valve piston, preferably by a machining process, in order to complete the two annular sealing sections.
  • Alternatives would be, for example, a smoothing process such as polishing.
  • the supposed one is The disadvantage is that the outer annular sealing section, which is preferably formed from a plastic material, comes into contact with chips that are produced during the machining of the inner annular sealing section, which is preferably made of metal, in particular steel. Machining is carried out, for example, by grinding. Manufacturing tests have shown that with the selected material pairing, the metal chips did not have a negative effect on the plastic surface.
  • the invention further relates to a valve piston and/or a guide body for a previously described tank valve.
  • the valve piston and the guide body can be traded separately.
  • valve piston is preferably guided in the guide body in such a way that it can only move back and forth in the guide body in a translational manner.
  • a rotational decoupling of the valve piston advantageously ensures that the valve piston cannot rotate in the guide body during operation of the tank valve. This can further reduce wear in the area of the conical sealing seat. This can extend the service life of the tank valve.
  • Figure 1 is a sectional view of an unpublished tank ventilation valve in a closed position
  • Figure 2 is a sectional view of the tank ventilation valve from Figure 1 in a ventilation position
  • Figure 3 is a side view of a pressure tank with two tank valves
  • Figure 4 shows a guide body of a tank valve with an annular groove into which a sealing ring with a rectangular ring cross section is pressed, before final processing of the guide body with the sealing ring, in longitudinal section;
  • Figure 5 shows the guide body with the sealing ring after final processing, which is preferably carried out by machining, for example by grinding;
  • Figure 6 shows an enlarged detail from Figure 5 with the processed sealing ring
  • Figure 7 shows a tank valve designed, for example, as a tank ventilation valve with the guide body from Figure 5 in a longitudinal section;
  • Figure 8 shows an enlarged detail with the sealing ring from Figure 7;
  • FIG. 9 shows a further enlarged representation of the detail from FIG. 8, with an angular difference between two conical sealing surfaces of the conical sealing seat being shown enlarged for illustration
  • a tank valve 1 designed as a tank ventilation valve is shown schematically in longitudinal section in a closed position V.
  • the tank ventilation valve 1 has a base body 3, which extends along a longitudinal axis L and is essentially rotationally symmetrical.
  • the base body 3 is also referred to as a guide body.
  • a base body channel 5, also referred to as a guide recess, is formed in the base body 3 and extends along the longitudinal axis L through the entire base body 3.
  • the base body is screwed via a thread into a valve receptacle 4 of a pressure tank 2 (see FIG. 3), not shown.
  • the base body 3 is sealed to the valve receptacle 4 via two sealing devices 25.
  • the base body 3 has several different parts from an outer surface 13 of the Base body 3 has transverse feedthroughs 14 extending radially inwards into the base body channel 5 for passing the gas through in the venting position E (see FIG. 2).
  • the base body channel 5 has an internal thread 16.
  • a closure element 6 is arranged in the base body channel 5 and guided linearly in the base body channel 5.
  • the closure element 6, also referred to as a valve piston, has a closure end face 10 and a tank end face 20 opposite the closure end face 10, in which a spring receptacle 21 is formed.
  • a helical spring 22 is arranged in the spring receptacle 21, through which the closure element 6 can be pressed with a restoring force in the direction of the closure position V shown.
  • the coil spring 22 is supported against the valve seat 4 and is also referred to as a closing spring.
  • the closure element 6 has a recess 17 extending along the longitudinal axis L for discharging the gas.
  • a ventilation channel 7 of the ventilation valve 1 is formed by the recess 17 and the transverse passages 14.
  • the closure element 6 preferably has several, for example two, three or four, recesses 17.
  • the recesses are preferably arranged evenly distributed over the circumference of the closure element 6.
  • the recesses 17 are preferably
  • a second sealing surface 12 of the closure device 6 designed as an external sealing cone, lies flat against a first sealing surface 11 of the base body 3, designed as an internal sealing cone.
  • an actuating element 8 is arranged in the base body channel 5.
  • the actuating element 8 has an external thread 15, which is in engagement with the internal thread 16 of the base body channel 5.
  • a hexagon socket 26 for a tool is formed in the actuating element 8.
  • another geometry, such as a slot, Phillips, Torx or the like, can also be provided.
  • the actuating element 8 is sealed to the base body 3 via a sealing device 25.
  • a convexly curved actuation end face 9 of the actuation element 8 faces the closure end face 10 and is spaced from it. By further screwing the actuation element 8 into the base body channel 5, the actuation end face 9 can be pressed against the closure end face 10.
  • FIG 2 shows the tank ventilation valve 1 from Figure 1 in the ventilation position E schematically in a sectional view.
  • the actuating element 8 is screwed into the base body channel 5 in such a way that the actuating end face 9 presses against the closure end face 10 and the closure element 6 is thereby translated translationally into the venting position E.
  • the coil spring 22 is therefore further tensioned compared to the closed position V. Due to the self-locking between the internal thread 16 and the external thread 15, the actuating element 8 and the closure element 6 remain in the venting position E even when the tool is removed.
  • the translational displacement of the closure element 6 creates a gap between the first sealing surface 11 and the second sealing surface 12 and thus establishes fluid communication between the inlet bore 23 and the outlet bore 24 via the ventilation channel 7.
  • the gas can thus flow from the pressure tank 2 via the inlet bore 23, the recess 17 and the transverse passages 14 into the drain bore 24, so that the pressure tank 2 is vented in a targeted and low-wear manner in this way.
  • the sealing devices 25 prevent the gas from flowing between the base body 3 and the valve receptacle 4 and through the tank ventilation valve 1 into the surroundings of the pressure tank 2.
  • FIG 3 the preferred embodiment of the pressure tank 2 according to the invention is shown schematically in a side view.
  • the pressure tank 2 has a tank wall 18, through which a tank interior 19 is formed.
  • Two valve receptacles 4 are formed on the tank wall 18.
  • a tank ventilation valve 1 according to the invention is arranged in one of the valve receptacles 4.
  • there is one on the other valve receptacle 4 Interface can be arranged for coupling the pressure tank 2 to a hydrogen system.
  • the pressure tank 2 is preferably designed as a hydrogen tank for a motor vehicle.
  • FIGS. 4 to 6 A guide body 43 of a tank valve 41 shown in FIG. 7 is shown in FIGS. 4 to 6.
  • the tank valve 41 is, for example, a tank ventilation valve, as shown in Figures 1 to 3.
  • the claimed tank valve 41 essentially involves a conical sealing seat 50, which is shown enlarged in section in Figures 8 and 9.
  • the guide body 43 comprises a guide recess 45, in which a valve piston 46 is guided to be translationally movable back and forth along a longitudinal axis L which runs in the horizontal direction in FIGS. 4 to 7.
  • a closing body 47 is formed, which can also be referred to as a valve piston head.
  • the closing body or valve piston head 47 in cooperation with a closing end 48 of the guide body 43, represents the conical sealing seat 50, which can also be referred to as a valve seat.
  • the conical sealing seat or valve seat 50 comprises a sealing surface 51 formed on the valve piston 46 or the valve piston head or closing body 47, which comes into sealing contact with a sealing surface 52 in a closed state of the tank valve 41, which rests on the guide body 43 or on the closing end 48 of the Guide body 43 is formed.
  • the sealing surface 51 formed on the valve piston 46 is also referred to as the first sealing surface 51.
  • the sealing surface 52 formed on the guide body 43 is also referred to as the second sealing surface 52.
  • the valve body 46 is formed of a steel material.
  • the guide body 43 is also made of a steel material, but is combined in the area of the sealing surface 52 with a sealing body 57 made of a plastic material.
  • the sealing body 57 serves to represent a sealing ring and is received in an annular groove 56 which is formed in the sealing surface 52 of the guide body 43.
  • the sealing body 57 designed as a sealing ring, serves in the sealing surface 52 to represent an external Sealing section 54, which is arranged radially outside an inner sealing section 53 of the sealing surface 52.
  • a further sealing section 55 which, however, does not perform a sealing function, is arranged radially outside of the outer sealing section 54
  • the sealing sections 53 and 55 are formed from the steel material of the guide body 43.
  • the outer sealing section 54 consists of a plastic material from which the sealing body 57 is formed.
  • the plastic material is a polyimide. Depending on the medium, such as gas, and pressure, another plastic could also be suitable.
  • the conical sealing seat 50 is biased into its closed position by a closing spring 62. In the closed position, the sealing surfaces 51 and 52 are partially in contact with one another, sealing each other.
  • two arrows 38 and 39 indicate how a plastic ring, which serves to represent the sealing body 57 at the closing end 48 of the guide body 43, is pressed into an annular groove 56.
  • the plastic ring is made of a polyimide and has a rectangular ring cross section. The plastic ring is pressed firmly into the annular groove 56, which is formed on the closing end 48 of the guide body 43.
  • the guide body 43 As part of a final processing of the guide body 43, it is machined at its closing end 48 with the inserted plastic ring, preferably by grinding. The result of the machining is shown enlarged in Figures 6 and 8.
  • the sealing body 57 serves in the annular groove 56 at the closing end 48 of the guide body 43 to represent an outer sealing section 54.
  • the outer sealing section 54 is arranged radially outside an inner sealing section 53.
  • the sealing portion 53 is formed from the steel material from which the guide body 43 is formed.
  • a further sealing section 55 which is arranged radially outside the outer sealing section 54, is also formed from the steel material from which the guide body 43 is formed.
  • the sealing sections 53 and 55 delimit the annular groove in which the sealing body 57 is arranged.
  • the sealing section 54 is formed from the plastic material, which is machined together with the two sealing sections 53 and 55 during machining
  • the angle difference 65 is only one to three degrees or even less.
  • the two sealing surfaces 51 and 52 first come into contact with one another in a circular contact area 67, namely at an outer diameter 74 of the closing body 47 at the end of the valve piston 46.
  • the contact area 67 lies within the outer sealing section 54 of the sealing surface 52 In the enlarged view of Figure 9 you can see that this results in a sealing gap 66, which expands radially inwards starting from the contact area 67.
  • the angular difference in the sealing seat could also be reversed, that is, the closing body 47 would initially contact the sealing body 57 on a small inner diameter at small pressures. At higher pressures, the sealing area 55 would then have a supporting effect.
  • arrows 71 to 77 show a main inner diameter 71 of the guide recess 45 for the valve piston 46 in the guide body 43, an inner diameter 72 of the sealing surface 51, an additional inner diameter 73 of the outer sealing section 54, the outer diameter 74 of the sealing surface 51, an additional outer diameter 75 of the outer sealing section 54, a main outer diameter 76 of the sealing surface 52 and a guide body outer diameter 77 at the closing end 48 of the guide body 43 are indicated.
  • the sealing body 57 is prevented during operation of the tank valve is undermined by pressure. This reliably prevents leaks during operation of the tank valve 41.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)

Abstract

L'invention concerne une soupape de réservoir (1) pour un réservoir sous pression (2), ladite soupape de réservoir comprenant un corps de guidage (3) et un piston de soupape (4) qui est précontraint dans une position fermée par un ressort de fermeture (22) et qui est guidé dans un évidement de guidage (5) du corps de guidage de façon à être mobile en va-et-vient entre la position fermée et une position ouverte, un siège d'étanchéité conique de la soupape de réservoir comprenant une première et une seconde surface d'étanchéité conique qui viennent en contact d'étanchéité l'une avec l'autre lorsque le piston de soupape (4) adopte sa position fermée. Afin d'améliorer la soupape de réservoir en termes de bonne étanchéité du siège d'étanchéité conique pendant le fonctionnement à des pressions variant largement, au moins l'une des surfaces d'étanchéité comprend au moins deux parties d'étanchéité de type bague circulaire qui viennent en contact avec l'autre surface d'étanchéité conique en fonction de la pression de réservoir interne agissant sur le piston de soupape (4) dans la même direction que la force de précontrainte du ressort de fermeture (22).
PCT/EP2023/068374 2022-08-03 2023-07-04 Soupape de réservoir, et procédé de fabrication d'une soupape de réservoir WO2024028020A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022208068.8A DE102022208068A1 (de) 2022-08-03 2022-08-03 Tankventil und Verfahren zum Herstellen eines Tankventils
DE102022208068.8 2022-08-03

Publications (1)

Publication Number Publication Date
WO2024028020A1 true WO2024028020A1 (fr) 2024-02-08

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WO (1) WO2024028020A1 (fr)

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3890997A (en) * 1972-03-03 1975-06-24 Linde Ag Automatic pressure-control valve, especially for a pressurized-gas supply installation
US4827972A (en) * 1987-12-18 1989-05-09 Graham Larry V Priority flow control valve
EP0807226A1 (fr) * 1994-11-23 1997-11-19 Shell Internationale Researchmaatschappij B.V. Dispositif de decharge et de remplissage destine a une bouteille a gaz
US5836352A (en) * 1996-06-06 1998-11-17 Pgi International, Ltd. Environmental fill valve
EP1197691A2 (fr) * 2000-10-16 2002-04-17 Ventrex Automotive GmbH Soupape de remplissage
US7591450B1 (en) * 2001-04-16 2009-09-22 Blume George H Valve body and seal assembly
US20170254474A1 (en) * 2016-03-03 2017-09-07 Evoguard Gmbh Steam trap, aseptic double seated valve, method of operating the steam trap, and filling plant
US9909670B2 (en) * 2015-03-04 2018-03-06 Praxair Technology, Inc. Modified vacuum actuated valve assembly and sealing mechanism for improved flow stability for fluids sub-atmospherically dispensed from storage and delivery systems
KR101875420B1 (ko) * 2018-03-22 2018-07-06 박희성 소형 가스저장탱크용 멀티밸브장치
US20200149654A1 (en) * 2017-06-23 2020-05-14 Engineered Controls International, Llc Cryogenic cylinder control system, globe valve, and solenoid valve
KR102189473B1 (ko) * 2019-07-17 2020-12-11 박희성 가스저장탱크용 더블체크 멀티밸브장치

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3890997A (en) * 1972-03-03 1975-06-24 Linde Ag Automatic pressure-control valve, especially for a pressurized-gas supply installation
US4827972A (en) * 1987-12-18 1989-05-09 Graham Larry V Priority flow control valve
EP0807226A1 (fr) * 1994-11-23 1997-11-19 Shell Internationale Researchmaatschappij B.V. Dispositif de decharge et de remplissage destine a une bouteille a gaz
US5836352A (en) * 1996-06-06 1998-11-17 Pgi International, Ltd. Environmental fill valve
EP1197691A2 (fr) * 2000-10-16 2002-04-17 Ventrex Automotive GmbH Soupape de remplissage
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