EP1082560B1 - Unite de commande pour une soupape de surete - Google Patents

Unite de commande pour une soupape de surete Download PDF

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Publication number
EP1082560B1
EP1082560B1 EP99936331A EP99936331A EP1082560B1 EP 1082560 B1 EP1082560 B1 EP 1082560B1 EP 99936331 A EP99936331 A EP 99936331A EP 99936331 A EP99936331 A EP 99936331A EP 1082560 B1 EP1082560 B1 EP 1082560B1
Authority
EP
European Patent Office
Prior art keywords
pressure
converter
line
bellows
control device
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 - Lifetime
Application number
EP99936331A
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German (de)
English (en)
Other versions
EP1082560A2 (fr
Inventor
Hermann-Josef Conrads
Erwin Laurer
Jürgen MODEL
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Areva GmbH
Original Assignee
Framatome ANP 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 Framatome ANP GmbH filed Critical Framatome ANP GmbH
Publication of EP1082560A2 publication Critical patent/EP1082560A2/fr
Application granted granted Critical
Publication of EP1082560B1 publication Critical patent/EP1082560B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/0426—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with fluid-operated pilot valves, i.e. multiple stage valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type
    • Y10T137/7769—Single acting fluid servo

Definitions

  • the invention relates to a control device with a Pressure-displacement converter in which a pressure difference between one Pressure room and a separate other room in one movement of an actuator can be implemented, with the actuator a control part for controlling a safety valve of a pressure vessel can be triggered, and wherein the pressure vessel via a pressure tapping line with the pressure chamber and the other room via a drainage line with a blow-off tank is connectable.
  • Control devices for controlling a safety valve known. These are spring-loaded control valves, i.e. control valves that work on the principle of rest. They have a valve spring against a hydraulic one Force acts which results from the system pressure of the to be secured System which is for example a pressure vessel derives. Such control valves are therefore only by actuated the system pressure so that external energy supply through e.g. motor, magnetic, pneumatic or hydraulic Facilities is not mandatory.
  • the first line is one Pressure tapping line (measuring line) with which the control valve can be acted upon with the system pressure in the pressure vessel.
  • the second line is a control line through which the control valve acts on the safety valve.
  • the third line is a drainage line (Discharge line), which either leads to the atmosphere or - especially in nuclear plants - in a blow-off tank (Pressure holder blow-off tank) opens.
  • Drain line Drain line
  • Relieve a safety valve that works according to the relief principle via the control line and the drainage line held in the blow-off tank.
  • a pressure-path converter in which there is a pressure difference between one pressure room and another separate from it Space can be implemented in a movement of an actuator.
  • the pressure tapping line opens into the pressure chamber.
  • the pressure-displacement converter DE 39 06 888 C2 has one in a cylinder led converter piston, with the pressure in the pressure chamber is acted upon.
  • the pressure-path converter of DE 196 28 610 C1 is equipped with a converter bellows, the interior of which forms the pressure chamber.
  • the pressure-path converter the pressure difference between the pressure chamber and the another room converted into a movement of the actuating body, wherein the actuating body in particular by the converter piston or is formed by a bellows head of the converter bellows.
  • the Actuator acts on a control part via a tappet for example the discharge of one according to the discharge principle safety valve triggers.
  • the control section DE 196 28 610 C1 includes a "pilot part” and an immediate acting on the safety valve "Controller".
  • Control valves are disadvantageously sensitive to an increase in pressure in this blow-off tank.
  • a short-lived but strong one Pressure increase could arise there, for example, if in in the event of a malfunction, the pressure in the blow-off tank is the design value exceeds, so that one of the pressure protection of the blow-off tank serving bursting membrane breaks.
  • Such an increase in pressure could lead to the unwanted premature closing of a open, i.e. blow off, lead safety valve.
  • Even a lower pressure increase in the blow-off tank can be disadvantageous Affect the function of the control valve, because the response pressure for the Opening of the activated safety valve has changed significantly can be.
  • the invention has for its object a control device to specify for a safety valve that is opposite a Pressure increase in the blowdown tank is insensitive, and at in particular an unwanted closing of an opened safety valve or influencing the response pressure for opening a safety valve due to an increase in pressure is safely avoided in the blow-off tank.
  • the object is achieved according to the invention in a first embodiment solved in that one associated with the drainage line Switchover valve device is present, one of which Drain line goes out, with a pressure in the blow-off tank above a limit pressure by the switching valve device the other room with the discharge pipe instead of the blow-off tank connected is.
  • control device is a excessive pressure in the blow-off tank is kept away from the pressure-displacement converter, while ensuring that a Fluid flow from the other room through the discharge line is possible.
  • the discharge line can, for example, in the always depressurized system drainage system of a nuclear System.
  • the switching valve device can, for example, at least partially arranged in the drainage line.
  • the discharge line can be switched from the Branch off the drainage line.
  • the changeover valve device comprises a drainage valve device arranged in the drainage line and a discharge valve device arranged on the discharge line.
  • the drainage valve device and / or the Discharge valve device in a starting position of the actuating body, in which the control part is not triggered, closed This ensures that the other one in normal operation Space is isolated from the blow-off tank.
  • Normal operation means that the safety valve is closed, i.e. that at a safety valve working according to the relief principle do not discharge any fluid flow (drainage) from the control device is.
  • the closing force is Drainage valve device smaller than a closing force of the AbGermanventil beautifully.
  • the object is achieved according to the invention in a second embodiment solved by a with the blow-off tank via a compensating line connectable hydraulic compensation system, that from a pressure in the blow-off tank a first force on the Actuator generated, which one of this pressure in the other Counteracts space generated second force on the actuator.
  • the second embodiment offers in contrast to the first embodiment, the additional advantage that an active outflow of fluid (drainage) into a Space outside the blow-off tank does not occur.
  • a pressure-displacement transducer is based on both embodiments understood every system according to the invention, at which a pressure change, in particular a pressure increase, in a change of location of an actuator can be implemented independently whether the change of location steadily increases with pressure or takes place suddenly at a certain limit pressure.
  • the safety valve of one of the two embodiments can work especially on the principle of relief or burden, the control by the control part to relieve or loading and thus to open the safety valve leads.
  • control body is in one of the two embodiments with a converter piston and / or a first one Conversion bellows in connection with the pressure in the other Space can be acted upon and by or which the second force can be generated.
  • the hydraulic compensation system comprises a compensation piston and / or a compensatory bellows, which with the Pressure in the blow-off tank can be acted upon, and by which the first force can be generated.
  • the first force is special mechanically from the compensating piston or from the compensating bellows transferable to the actuator.
  • the Diameter of the compensating piston and / or the compensating bellows essentially the diameter of the converter piston or the first converter bellows.
  • the compensating piston or the compensating bellows are preferred movably arranged along an axis along which the Adjusting body is movable. This ensures that the first produced on the compensating piston or on the compensating bellows Force the actuator body in a simple and reliable manner is transferable.
  • the compensating piston or the compensating bellows are special arranged in series with the control body.
  • Such a straight forward Series arrangement has the advantage that hydraulic compensation system easily and quickly to an existing one Control device without hydraulic compensation system can be retrofitted.
  • the compensating piston or compensating bellows is preferred a grip-like driver for the converter piston or one of the converter bellows.
  • the drainage line is and / or the compensation line from the hydraulic compensation system seen from a slope.
  • penetrated pressure medium e.g. Condensate
  • the first force e.g. by the driver, on the converter piston or one of the Transfer bellows and, unless they themselves the Form control body, transferred to the separate control body.
  • the pressure vessel 1 shows, as a system to be protected, a pressure vessel 1, to which a safety valve 4 working according to the relief principle is assigned, which relieves the pressure vessel 1 via a blow-off line 6 when the system pressure p s rises above a previously set limit value.
  • the pressure vessel 1 is, for example, a nuclear reactor pressure vessel.
  • the opening of the safety valve 4 is done by controls a control device designated overall by 10, via a control line 11 to the safety valve 4 acts.
  • the control device 10 is based on the Principle of a spring-loaded control valve based on the principle of rest and comprises three assemblies, namely a pressure-displacement converter 12 and a control part 14, which in turn consists of a Pilot part 16 and a main control part 18 is formed.
  • the three modules are housed in a common housing 19.
  • the pressure vessel 1 is connected via a pressure tapping line 20 to a pressure chamber 22 of the pressure-displacement converter 12.
  • the pressure chamber 22 is part of a cylinder 24 in which an actuating body 26, here a conversion piston 26A, can be moved and which separates the pressure chamber 22 from another chamber 28.
  • the actuating body 26 acts on the pilot part 16 via a plunger 30.
  • the actuating body 26 or the converter piston 26A is pressed down in FIG. 1 by a first spring 32, which rests on a plate 34.
  • Figure 1 shows the actuator 26 in a starting position in which the control part 14 is not triggered.
  • the pilot part 16 has a filling cone 40 and one Relief cone 42 on.
  • the filler cone 40 is over a lower extension 44, an upper extension 46 and over Sealing elements 48, 49 guided in a cylinder in the housing 19.
  • the filling cone 40 is by a second spring 50 in Figure 1 pressed down.
  • the relief cone 42 which has a third spring 54 also - with reference to Figure 1 - is pressed down.
  • the safety valve 4 shown in FIG. 1 blows off into the blow-off tank 92 via the blow-off line 6.
  • Other safety valves can also blow off into the blow-off tank 92. This can lead to an undesired pressure increase in the blow-off tank 92 (pressure p T ), which would also affect the other space 28 of the pressure-displacement converter 12 (pressure P A ) and could influence its function.
  • the control device shown in FIG. 1 has a changeover valve device 100, from which a discharge line 102 extends.
  • the changeover valve device 100 interrupts the connection of the other space 28 to the blowdown tank 92 and instead establishes a connection of the other space 28 to the discharge line 102, which is not shown in a drawing always unpressurized space flows.
  • FIG. 2 shows a special embodiment of the changeover valve device 100 shown in detail and enlarged. It consists of one arranged in the drainage line 90 Drainage valve device 106 and from one of the discharge line 102 associated discharge valve device 108.
  • the drain valve device 106 and the purge valve device 108 each consist of a parallel connection of two valves connected in series. This is a subordinate Individual errors of a valve both in the open and also in the closed position of both the drainage valve device 106 and the discharge valve device 108 can be controlled.
  • valves are only shown schematically in FIG. 2. They have a seat 110, onto which a valve cone 112 is pressed by a spring 114.
  • the closing force of the valves in the discharge valve device 108 is greater than that of the valves in the drainage valve device 106. If the pressure p T in the blow-off tank 92 increases undesirably during relief via the drain line 90 into the blow-off tank 92, the valves in the drainage valve device 106 first close, before the valves in the discharge valve device 108 open at a slightly higher pressure in the drain line 90 and relief is made possible via the discharge line 102. When the undesired pressure increase has decreased again, the connection to the blow-off tank 92 is released again.
  • FIG. 3 is a second embodiment of a control device 10 according to the invention shown in place the switching valve device a hydraulic compensation system 200 for "back pressure compensation" and otherwise largely identical to the control device 10 of FIG. 1 is.
  • the compensation system 200 comprises a compensation piston 210, which is movable in a cylinder 212.
  • the balance piston 210 is symmetrical with respect to an axis 213 and movable along this axis, along which the converter piston 26A is movable.
  • the compensation piston 210 is sealed against the cylinder 212 via a sealing ring 214 and with a cylinder body 217 in a guide 218 in Housing 19 of the control device 10 out.
  • the housing 19 is compared to the embodiment shown in Figure 1 beyond the plate 34 (see Figure 1) downwards extended.
  • a first bore 220 connects one of the balance pistons 210 formed in the cylinder 212 first chamber 222 with a not shown, always depressurized space, for example with the system drainage system of a nuclear plant.
  • the first chamber 222 can also contain the nuclear facility to be connected. From the first chamber 222 could only leakage flows of the used anyway Eject seals or bellows.
  • a compensation line 224 designed as a second bore connects a second chamber 226, which is also from the balance piston 210 is formed in the cylinder 212 with which Drainage line 90.
  • An undesired increase in pressure in the blow-off tank 92 affects the second chamber 226 as well as the other space 28 in the same way.
  • the equalizing piston 210 which is acted upon by the pressure P T in the blow-off tank 92 via the second chamber 226, then generates a first force (directed upwards in FIG. 3), which acts on the actuating body 26 via a piston extension 230, the plate 34 and a converter pin 235 is transferred to the converter piston 26A.
  • the first force equals an undesired second generated by the pressure P T in the blow-off tank 92 via the other chamber 28 on the converter piston 26A Force (directed downwards in FIG. 3) completely, so that the movement of the converter piston 26A under the influence of the system pressure p s in the pressure chamber 22 (pressure p D ⁇ p s ) is unaffected by the pressure increase in the blow-off tank 92.
  • FIG 4 shows a fourth embodiment of a control device 10 according to the invention, which is also a hydraulic Compensation system 200 includes. Compensation system 200 is drawn enlarged in Figure 5. Those parts of the Control device 10, which is not the compensation system 200 concern are already in the German patent specification DE 196 28 610 C1, column 3, line 29, to column 6, line 57, described. This section of text from DE 196 28 610 C1 is part of the present patent application.
  • the system pressure p s of the pressure container acts on the interior of converter bellows 302 and 320.
  • the interior of the first converter bellows 302 forms a first one Pressure chamber 300, which by the first converter bellows 302 of a first other room 303 is separated.
  • the first converter bellows 302 is at its lower end with a flange 304 welded. At its upper end it is with one Bellows head 306 connected, which is essentially the actuating body 26 forms.
  • This bellows head 306 has in its upper section a guide bearing 308.
  • the bellows head 306 can be a comprise lower cylindrical part 310 on which the first converter bellows 302 is performed. When the device is depressurized this cylindrical part 310 on the front on cams 312 of Fit flange 304.
  • a second transducer bellows 320 is located on the flange 304 from below welded, the interior of a second pressure chamber 322 forms and the second pressure chamber 322 of a second separates other room 323.
  • the second converter bellows 320 is on its opposite, lower end with a screw-in part 325 welded to the lower end of the cylindrical Part 310 of the bellows head 306 is connected. This connection can be a thread.
  • the screw-in part 325 has a guide bearing 327.
  • the lower end of the screw-in part 325 is threaded provided, by means of a nut 329 and a pressure piece 331 a biasing force is applied to a spring 333 can be.
  • the spring 333 is supported on the flange 304.
  • the Spring 333 is preloaded and forms a counterforce to one Hydraulic force caused by the medium from the pressure tapping line 20 acts on the first converter bellows 302.
  • the hydraulic power acts on the second converter bellows 320 in the same direction as the force of spring 333
  • Pressure in pressure vessel 1 maintain the hydraulic force on the first converter bellows 302 on the one hand and the Sum of the hydraulic force on the second converter bellows 320 and the spring force of the spring 333 balance.
  • the hydraulic balancing system 200 includes the one in FIG 4 and 5 embodiment shown a compensating ring piston 350, which encloses the second converter bellows 320 is arranged.
  • the compensating ring piston 350 has in FIGS. 4 and 5 example shown in the lower part a narrow part 350B and in the upper part a wide part 350A.
  • the compensating ring piston 350 acts via an under-grip driver 352 on the narrow part 350B on an extension 354 on the screw-in part 325.
  • the compensating ring piston 350 is shown enlarged in FIG.
  • the compensation ring piston 350 is connected to the drainage line 90 via a compensation line 224 designed as a bore.
  • the diameter d A of the wide part 350A of the compensating ring piston corresponds to the hydraulic diameter (taking into account the larger wetted area of a bellows compared to a piston of the same diameter) of the first converter bellows 302. Since both the compensating ring piston 350 and the first converter bellows 302 are increased by a possibly increased one Pressure in the drain line 90 are applied, a force equalization is effected in the pressure-displacement converter 12.
  • the pressurized from the drain line 90 Part of the balancing ring piston 350 is opposite the rest Part of the pressure-displacement converter 12 by sealing elements 356, 358, 360 and 362 sealed.
  • the sealing elements are in pairs Double seal 356, 360 and 358, 362 arranged.
  • the space between two sealing elements arranged as double seals, e.g. e.g. the space between the sealing element 356 and the Sealing element 360, is with holes 364 and 366 respectively Always depressurized, not drawn space, especially with the plant drainage system of a nuclear plant, connected.
  • the rest of the pressure-displacement converter 12 is standing via a line 368 to the atmosphere or to the containment the nuclear facility in connection.

Claims (13)

  1. Unité (10) de commande
    comportant un convertisseur (12) pression-course, dans lequel une différence (pD- pA) de pression entre une chambre (22) de pression et une autre chambre (28) séparée de celle-ci peut être transformée en un déplacement d'un corps (26) d'actionnement,
    le corps (26) d'actionnement permettant de déclencher une partie (14) de commande pour asservir une soupape (4) de sûreté d'un récipient (1) sous pression,
    et le récipient (1) sous pression pouvant être relié par l'intermédiaire d'une conduite (20) de soutirage de pression à la chambre (22) de pression et
    l'autre chambre (28) pouvant être reliée par l'intermédiaire d'une conduite (90) de drainage à un réservoir (92) de purge,
    caractérisée par un ensemble (100) de soupape de commutation, associé à la conduite (90) de drainage et duquel part une conduite (102) d'évacuation, l'autre chambre (28) étant, au moyen de l'ensemble (100) de soupape de commutation, reliée au lieu du réservoir (92) de purge à la conduite (102) d'évacuation si la pression dans le réservoir (92) de purge est supérieure à une pression limite.
  2. Unité de commande suivant la revendication 1, caractérisée en ce que l'ensemble (100) de soupape de commutation comprend un ensemble (106) de soupape de drainage disposé dans la conduite (90) de drainage et un ensemble (108) de soupape d'évacuation disposé dans la conduite (102) d'évacuation.
  3. Unité de commande suivant la revendication 2, caractérisée en ce que l'ensemble (106) de soupape de drainage et/ou l'ensemble (108) de soupape d'évacuation sont fermés dans une position initiale du corps (26) d'actionnement, dans laquelle la partie (14) de commande n'est pas déclenchée.
  4. Unité de commande suivant la revendication 3, caractérisée en ce qu'une force de fermeture de l'ensemble (106) de soupape de drainage est inférieure à une force de fermeture de l'ensemble (108) de soupape d'évacuation.
  5. Unité (10) de commande
    comportant un convertisseur (12) pression-course, dans lequel une différence (pD- pA) de pression entre une chambre (22 ; 300) de pression et une autre chambre (28 ; 303) séparée de celle-ci peut être transformée en un déplacement d'un corps (26) d'actionnement,
    le corps (26) d'actionnement permettant de déclencher une partie (14) de commande pour asservir une soupape (4) de sûreté d'un récipient (1 ) sous pression,
    et le récipient (1) sous pression pouvant être relié par l'intermédiaire d'une conduite (20) de soutirage de pression à la chambre (22 ; 300) de pression et
    l'autre chambre (28 ; 303) pouvant être reliée par l'intermédiaire d'une conduite (90) de drainage à un réservoir (92) de purge,
    caractérisée par un système (200) de compensation hydraulique, pouvant être relié au réservoir (92) de purge par l'intermédiaire d'une conduite (224) de compensation et qui produit sur le corps (26) d'actionnement, à partir d'une pression (pT) dans le réservoir (92) de purge, une première force qui s'oppose à une deuxième force produite sur le corps (26) d'actionnement par cette pression (pT) dans l'autre chambre (28 ; 303).
  6. Unité de commande suivant la revendication 5, caractérisée en ce que le corps (26) d'actionnement est relié à un piston (26A) de convertisseur et/ou à un premier soufflet (302) de convertisseur, qui peut/peuvent être sollicité(s) par la pression (PA) dans l'autre chambre (28; 303) et par lequel/lesquels la deuxième force peut être produite.
  7. Unité de commande suivant la revendication 5 ou 6, caractérisée en ce que le système (200) de compensation hydraulique comprend un piston (210 ; 350) de compensation et/ou un soufflet de compensation, qui peut être sollicité par la pression (pT) dans le réservoir (92) de purge et par lequel la première force peut être produite.
  8. Unité de commande suivant les revendications 6 et 7, caractérisée en ce que le diamètre (dA) du piston (210 ; 350) de compensation et/ou du soufflet de compensation correspond pour l'essentiel au diamètre (ds) du piston (26A) de convertisseur ou encore du premier soufflet (302) de convertisseur.
  9. Unité de commande suivant la revendication 7 ou 8, caractérisée en ce que le piston (210 ; 350) de compensation et/ou le soufflet de compensation sont disposés à déplacement le long d'un axe (213) le long duquel le corps (26) d'actionnement est également mobile.
  10. Unité de commande suivant l'une des revendications 7 à 9, caractérisée en ce que le piston (210) de compensation ou encore le soufflet de compensation est disposé en série avec le corps (26) d'actionnement.
  11. Unité de commande suivant la revendication 6 et l'une des revendications 7 à 9, caractérisée en ce que le piston (350) de compensation ou encore le soufflet de compensation est disposé en entourant au moins partiellement le piston de convertisseur ou encore le premier soufflet de convertisseur, ou un deuxième soufflet (320) de convertisseur.
  12. Unité de commande suivant la revendication 11, caractérisée en ce que le piston (350) de compensation ou encore le soufflet de compensation comporte un entraíneur (352) du genre à prise par en dessous pour le piston de convertisseur ou encore pour un (320) des soufflets de convertisseur.
  13. Unité de commande suivant l'une des revendications 5 à 12, caractérisée en ce que la conduite (90) de drainage et/ou la conduite (224) de compensation est/sont posée(s) en pente descendante, en vue depuis le système (200) de compensation hydraulique.
EP99936331A 1998-06-02 1999-05-27 Unite de commande pour une soupape de surete Expired - Lifetime EP1082560B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE1998124494 DE19824494C1 (de) 1998-06-02 1998-06-02 Steuereinrichtung für ein Sicherheitsventil
DE19824494 1998-06-02
PCT/DE1999/001560 WO1999063250A2 (fr) 1998-06-02 1999-05-27 Unite de commande pour une soupape de surete

Publications (2)

Publication Number Publication Date
EP1082560A2 EP1082560A2 (fr) 2001-03-14
EP1082560B1 true EP1082560B1 (fr) 2002-09-25

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EP99936331A Expired - Lifetime EP1082560B1 (fr) 1998-06-02 1999-05-27 Unite de commande pour une soupape de surete

Country Status (6)

Country Link
US (1) US6386228B2 (fr)
EP (1) EP1082560B1 (fr)
JP (1) JP3693917B2 (fr)
DE (2) DE19824494C1 (fr)
RU (1) RU2215223C2 (fr)
WO (1) WO1999063250A2 (fr)

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RU2792717C1 (ru) * 2022-08-15 2023-03-23 Акционерное общество "Конструкторское бюро химического машиностроения имени А.М. Исаева" Клапан газовый гидроуправляемый

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CN101876388B (zh) * 2009-05-01 2014-05-07 丛洋 减压阀、压缩气体供气系统及制冷系统
US20110226354A1 (en) * 2010-03-17 2011-09-22 Petur Thordarson Flow Controller
RU180055U1 (ru) * 2017-09-28 2018-05-31 Общество с ограниченной ответственностью "Научно-исследовательский инжиниринговый центр арматуростроения" (ООО НИИЦА) Автоматический защитный клапан прямого действия
RU2687198C1 (ru) * 2018-08-03 2019-05-07 Федеральное государственное автономное образовательное учреждение высшего образования "Сибирский федеральный университет" Способ управления клапанами импульсно-предохранительного устройства и устройство для его осуществления
CN117619320A (zh) * 2024-01-23 2024-03-01 潍坊中汇化工有限公司 一种乙腈制备用排压式反应釜

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RU2792717C1 (ru) * 2022-08-15 2023-03-23 Акционерное общество "Конструкторское бюро химического машиностроения имени А.М. Исаева" Клапан газовый гидроуправляемый

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JP3693917B2 (ja) 2005-09-14
US6386228B2 (en) 2002-05-14
WO1999063250A2 (fr) 1999-12-09
WO1999063250A3 (fr) 2000-02-17
JP2002517680A (ja) 2002-06-18
RU2215223C2 (ru) 2003-10-27
DE59902852D1 (de) 2002-10-31
EP1082560A2 (fr) 2001-03-14
DE19824494C1 (de) 1999-08-19
US20010006078A1 (en) 2001-07-05

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