EP1082560A2 - Unite de commande pour une soupape de surete - Google Patents

Unite de commande pour une soupape de surete

Info

Publication number
EP1082560A2
EP1082560A2 EP99936331A EP99936331A EP1082560A2 EP 1082560 A2 EP1082560 A2 EP 1082560A2 EP 99936331 A EP99936331 A EP 99936331A EP 99936331 A EP99936331 A EP 99936331A EP 1082560 A2 EP1082560 A2 EP 1082560A2
Authority
EP
European Patent Office
Prior art keywords
pressure
bellows
blow
control device
line
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.)
Granted
Application number
EP99936331A
Other languages
German (de)
English (en)
Other versions
EP1082560B1 (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
Siemens AG
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 Siemens AG filed Critical Siemens AG
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

Links

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 transducer in which a pressure difference between a pressure chamber and another space separated from it can be converted into a movement of an actuating body, with the actuating body being able to trigger a control part for actuating a safety valve of a pressure vessel, and wherein the pressure vessel is connected via a pressure tapping line the pressure chamber and the other room can be connected to a blow-off tank via a drainage line.
  • Control devices for controlling a safety valve are known from DE 39 06 888 C2 and from DE 196 28 610 Cl. These are spring-loaded control valves, i.e. control valves that work on the principle of rest. They have a valve spring which acts against a hydraulic force which is derived from the system pressure of the system to be protected, which is, for example, a pressure vessel. Such control valves are operated solely by the system pressure, so that external energy supply by e.g. Motor, magnetic, pneumatic or hydraulic devices are not absolutely necessary.
  • the first line is a pressure tapping line (measuring line) with which the system pressure in the pressure vessel can be applied to the control valve.
  • the second line is a control line through which the control valve acts on the safety valve.
  • the third line is a drainage line (blow-out line), which either leads to the atmosphere or - especially in nuclear facilities - into a blow-off tank (Pressure holder blow-off tank) opens.
  • the relief of a safety valve operating on the relief principle takes place via the control line and the drainage line into the blow-off tank.
  • a pressure-displacement transducer In which a pressure difference between a pressure space and another space separated from it can be converted into a movement of an actuating body.
  • the pressure tapping line opens into the pressure chamber.
  • the pressure-displacement converter of DE 39 06 888 C2 has a converter piston which is guided in a cylinder and can be acted upon by the pressure in the pressure chamber.
  • the pressure-displacement converter of DE 196 28 610 Cl is equipped with a converter bellows, the interior of which forms the pressure chamber.
  • the pressure difference between the pressure space and the other space is converted into a movement of the actuating body in the pressure-displacement transducer, the actuating body being formed in particular by the transducer piston or by a bellows head of the transducer bellows.
  • the actuating body acts via a tappet on a control part which, for example, triggers the relief of a safety valve operating on the relief principle.
  • the control part of DE 196 28 610 Cl includes a "pilot part” and a "control part” acting directly on the safety valve.
  • the control valves mentioned are disadvantageously sensitive to a pressure increase in this blow-off tank.
  • a short-lived but strong pressure rise could arise there, for example, if the pressure in the blow-off tank exceeds the design value in the event of a malfunction, so that a bursting membrane serving to protect the pressure of the blow-off tank breaks.
  • Such an increase in pressure could lead to the unwanted premature closing of an opened, ie, bleeding, safety valve.
  • a lower pressure increase in the blow-off tank can also be disadvantageous. have an impact on the function of the control valve, since the response pressure for opening the actuated safety valve can be changed significantly via the drainage line.
  • Such a rather slight increase in pressure in the blow-off tank can be caused, for example, by blowing off a safety valve if - as is usual in nuclear plants - the blow-off takes place via a blow-off line into the blow-off tank.
  • a safety valve that is just blowing off could also disadvantageously change the response pressure of another safety valve that is still closed.
  • the invention has for its object to provide a control device for a safety valve, which is insensitive to a pressure increase in the blow-off tank, and in particular an undesired closing of an opened safety valve or influencing the response pressure for opening a safety valve by a pressure increase in the blow-off tank safely avoided is.
  • the object is achieved in a first embodiment in that there is a changeover valve device assigned to the drainage line, from which a discharge line emanates, with the pressure in the blowdown tank above a limit pressure by the changeover valve device causing the other space to be used instead of the blowdown tank the discharge line is connected.
  • the discharge line can, for example, open into the always depressurized system drainage system of a nuclear system.
  • the switching valve device can, for example, be arranged at least partially in the drainage line.
  • the discharge line can branch off from the drain line via the switching valve device.
  • 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 is closed in an initial position of the actuating body in which the control part is not triggered. This ensures that the other room is insulated from the blow-off tank during normal operation. Normal operation means that the safety valve is closed, i.e. that in a safety valve operating according to the relief principle, no fluid flow (drainage) is to be removed from the control device.
  • the closing force of the drainage valve device is smaller than a closing force of the discharge valve device.
  • the object is achieved in a second embodiment by a hydraulic compensation system which can be connected to the blow-off tank via a compensating line and which generates a first force on the actuating body from a pressure in the blow-off tank, which force generates one of these pressures in the other room counteracts second force on the actuator.
  • the undesired second force does not influence the pressure-displacement transducer, or at least does not influence it in an undesired manner.
  • the second embodiment offers the additional advantage that active fluid outflow (drainage) does not occur in a space outside the blow-off tank.
  • a pressure-displacement transducer is understood to mean any system in relation to both embodiments according to the invention, in which a change in pressure, in particular an increase in pressure, a change in location of an actuator can be implemented, irrespective of whether the change in location is continuously increasing with pressure or erratic takes place at a certain limit pressure.
  • the safety valve of one of the two embodiments can work in particular according to the relief or loading principle, the activation by the control part leading to relief or loading and thus to the opening of the safety valve.
  • the actuator is connected to a converter piston and / or a first converter bellows, which can be acted upon by the pressure in the other space and by which the second force can be generated.
  • the hydraulic compensation system comprises a compensation piston and / or a compensation bellows which can be acted upon by the pressure in the blow-off tank and by means of which the first force can be generated.
  • the first force can in particular be transferred mechanically from the compensating piston or from the compensating bellows to the actuator.
  • the diameter of the compensating piston and / or the compensating bellows essentially corresponds to the diameter of the converter piston or of the first converter bellows.
  • the compensating piston or the compensating bellows are preferably arranged to be movable along an axis along which the actuator can also be moved. This ensures that the first force m generated on the compensating piston or on the compensating bellows can be transferred to the actuator in a simple and reliable manner.
  • the compensating piston or the compensating bellows are arranged, in particular, in a row to the actuating body.
  • Such a straight-line hermemander arrangement has the advantage that the hydraulic compensation system can be easily and quickly retrofitted to an existing control device without a hydraulic compensation system.
  • the compensating piston or the compensating bellows is arranged at least partially enclosing the converter piston or the first converter bellows or a second converter bellows.
  • the hydraulic compensation system can be integrated into the control device for the safety valve in a particularly space-saving and compact manner.
  • the compensating piston or compensating bellows preferably has an engaging driver for the converting piston or one of the converting bellows.
  • the drainage line and / or the compensation line is laid with a slope as seen from the hydraulic compensation system.
  • the first force e.g. by the driver, transferred to the converter piston or one of the converter bellows and, insofar as these do not form the actuating body itself, transferred to the separate actuating body.
  • FIGS. 1 to 5 Three exemplary embodiments of a control device according to the invention are explained in more detail with reference to FIGS. 1 to 5. It shows - each in a more or less schematic form:
  • FIG. 1 shows a first embodiment of a control device according to the invention in the first embodiment
  • FIG. 2 shows a detail from FIG. 1, 3 shows a second exemplary embodiment of a control device according to the invention in the second embodiment,
  • FIG. 4 shows a third embodiment of a control device according to the invention in the second embodiment
  • FIG. 5 shows an enlarged detail from FIG. 4.
  • FIG. 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 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.
  • control device 10 which acts on the safety valve 4 via a control line 11.
  • the control device 10 is based on the principle of a spring-loaded control valve according to the resting principle and comprises three assemblies, namely a pressure-displacement converter 12 and a control part 14, which in turn is formed from a pilot control part 16 and a main control part 18.
  • 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 converter 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.
  • FIG. 1 shows the actuating body 26 in a starting position in which the control part 14 is not triggered.
  • the pilot part 16 has a filling cone 40 and a relief cone 42.
  • the filler cone 40 is guided in a cylinder in the housing 19 via a lower extension 44, an upper extension 46 and via sealing elements 48, 49.
  • the filling cone 40 is pressed down by a second spring 50 in FIG. 1.
  • the relief cone 42 In the interior of the filling cone 40 is the relief cone 42, which is also pressed down by a third spring 54, based on FIG. 1.
  • the relief cone 42 When the pilot part 16 is triggered, the relief cone 42 is lifted from its seat by the plunger 30, so that the main control part 18 is relieved and thus the safety valve 4 is also relieved.
  • the relief acts via a relief bore 57 and a relief channel 58 on a non-return cone 80 of the main control part 18.
  • the fluid flowing through the relief channel 58 during the relief flows past the relief cone 42 along an annular space 85 around the tappet 30 into the other space 28 and from there via a drain line 90 into a blow-off tank 92.
  • the filler cone 40 While the main control part 18 and the safety valve 4 are being relieved, the filler cone 40 bears against its seat (upper) in the housing 19 in FIG. 1 (an abutment at the lower stop is shown), so that the system pressure in the pressure vessel 1 does not or no longer acts on the main control part 18.
  • 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 ⁇ ), 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 switch-over valve device 100 interrupts the connection of the other space 28 to the blow-off tank 92 and instead establishes a connection of the other space 28 with the discharge line 102, which is not shown in a always unpressurized space flows.
  • FIG. 2 shows a special embodiment of the changeover valve device 100 in detail and enlarged. It consists of a drainage valve device 106 arranged in the drainage line 90 and of a drainage valve device 108 assigned to the discharge line 102.
  • the drainage valve device 106 and the discharge valve device 108 each consist of a parallel connection of two valves connected in series. As a result, an assumed individual fault of a valve, both in the open and in the closed position, of both the drain valve and ⁇ chtung 106 and the discharge valve device 108 controllable.
  • valves are only shown schematically in FIG. 2. They have a seat 110 on which a valve cone 112 is pressed by a spring 114.
  • the closing force of the valves m the Abbowventilemcardi 108 is larger than that of the valves m the Dramageventilemcardi 106. If during a discharge through the drain line 90 m the blow-off tank 92, the pressure p ⁇ in the blow-off tank 92 undesirably increases initially close the valves m the Dramageventilemcardi 106, before the valves in the discharge valve device 108 open at a slightly higher pressure m 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 shows a second exemplary embodiment of a control device 10 according to the invention, which has a hydraulic compensation system 200 for “jerk pressure compensation” in place of the switching valve device and is otherwise largely identical to the control device 10 of FIG. 1.
  • the compensation system 200 comprises a compensation piston ben 210, which is movable in a cylinder 212.
  • the compensating piston 210 is symmetrical with respect to an axis 213 and can be moved along this axis, along which the converter piston 26A is also movable, and the compensating piston 210 is opposite the cylinder 212 via a sealing ring 214 sealed and guided with a cylinder body 217 m of a guide 218 in the housing 19 of the control device 10.
  • the housing 19 is extended downward beyond the plate 34 (see FIG. 1) compared to the exemplary embodiment shown in FIG.
  • a first bore 220 connects a first chamber 222 formed by the compensating piston 210 in the cylinder 212 to one not shown, always depressurized space, for example with the system drainage system of a nuclear plant.
  • the first chamber 222 can also be connected to the containment of the nuclear facility. In any case, only leakage flows of the seals or bellows used could emerge from the first chamber 222.
  • a compensation line 224 designed as a second bore connects a second chamber 226, which is also formed by the compensation piston 210 in the cylinder 212, to the drain line 90.
  • the first force is equal to an undesired one generated by the pressure p ⁇ in the blow-off tank 92 via the other space 28 on the converter piston 26A second 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 exemplary embodiment of a control device 10 according to the invention, which likewise comprises a hydraulic compensation system 200.
  • the compensation system 200 is shown enlarged in FIG.
  • Those parts of the control device 10 which do not relate to the compensation system 200 are already in the German patent specification DE 196 28 610 Cl, column 3, line 29, to column 6, line 57, described. This section of text from DE 196 28 610 Cl is part of the present patent application.
  • the system pressure p s of the pressure vessel acts on the interior of converter bellows 302 and 320.
  • the interior of the first converter bellows 302 forms a first pressure chamber 300, which is separated from the first other chamber 303 by the first converter bellows 302.
  • the first converter bellows 302 is welded to a flange 304 at its lower end. At its upper end it is connected to a bellows head 306, which essentially forms the actuator body 26.
  • This bellows head 306 has a guide bearing 308 in its upper section.
  • the bellows head 306 can comprise a lower cylindrical part 310, on which the first converter bellows 302 is guided. When the device is depressurized, this cylindrical part 310 can be seated on the end face on cams 312 of the flange 304.
  • a second transducer bellows 320 is welded to the flange 304 from below, the interior of which forms a second pressure space 322 and which separates the second pressure space 322 from a second other space 323.
  • the second converter bellows 320 is welded at its opposite, lower end to an unscrewing part 325, which is connected to the lower end of the cylindrical part 310 of the bellows head 306. This connection can be made via a thread.
  • the screw part 325 has a guide bearing 327 for the flange 304 hm.
  • the lower end of the screw-in part 325 is provided with a thread, by means of which a prestressing force can be applied to a spring 333 by means of a nut 329 and a pressure piece 331.
  • the spring 333 is supported on the flange 304.
  • the spring 333 is pretensioned and forms a counterforce to a hydraulic force which acts on the first converter bellows 302 through the medium from the pressure extraction line 20.
  • the hy Draulic force acts on the second converter bellows 320 in the same direction as the force of the spring 333. With the pressure in the pressure vessel 1 unchanged, the hydraulic force on the first converter bellows 302 and the sum of the hydraulic force on the second converter bellows 320 and the spring force remain the spring 333 the balance.
  • the hydraulic compensation system 200 comprises a compensation piston 350, which is arranged surrounding the second converter bellows 320.
  • the compensating piston 350 in the example shown in FIGS. 4 and 5 has a narrow part 350B in the lower part and a wide part 350A in the upper part.
  • the compensation piston 350 acts via an undergrip-like driver 352 on the narrow part 350B on an extension 354 on the screw-in part 325.
  • the compensation piston 350 is shown enlarged in FIG. 5 in the detail.
  • the compensation piston 350 is connected to the drainage line 90 via a compensation line 224 designed as a bore.
  • the diameter dp. of the broad part 350A of the compensating piston corresponds to the hydraulic diameter of the first converter bellows 302 (taking into account the larger wetted area of a bellows compared to a piston of the same diameter). Since both the compensating piston 350 and the first converter bellows 302 are caused by a possibly increased pressure m the drainage line 90 are acted upon, the pressure-displacement transducer 12 effects a force equalization.
  • the part of the compensating ring piston 350 acted upon by the pressure from the drain line 90 is sealed off from the remaining part of the pressure-displacement converter 12 by sealing elements 356, 358, 360 and 362.
  • the sealing elements are arranged in pairs as a double seal 356, 360 or 358, 362.
  • the space between two sealing elements arranged as a double seal, e.g. the space between the sealing element 356 and the sealing element 360 is connected via bores 364 and 366 to a space which is always depressurized and not shown, in particular the system drainage system of a nuclear facility.
  • the remaining part of the pressure-displacement converter 12 is connected via a line 368 to the atmosphere or to the containment of the nuclear facility.
  • the drainage line 90, the equalization line 224 and the bores 364, 366 mentioned in the last paragraph have a downward inclination - viewed from the inside of the control device 10 or pointing away from it

Abstract

L'invention concerne une unité de commande (10) dans laquelle un élément de commande (14) servant à commander une soupape de sûreté (4) d'un contenant sous pression (1) peut être déclenché par l'intermédiaire d'un capteur de pression-déplacement (12). Un compartiment (28; 303) du capteur de pression-déplacement (12) peut être relié à un réservoir d'évacuation (92) par l'intermédiaire d'une conduite d'évacuation (90). Un premier mode de réalisation de l'invention est caractérisé en ce qu'un système de soupape d'inversion (100) affecté à la conduite d'évacuation (90) relie le compartiment (28) non pas au réservoir d'évacuation (92) mais à une conduite d'évacuation (102) lorsque la pression dans le réservoir d'évacuation (92) est supérieure à une pression limite. Un deuxième mode de réalisation de l'invention comporte un système de compensation hydraulique (200) qui, à partir d'une pression dans le réservoir d'évacuation (92), exerce sur le capteur de pression-déplacement (12) une première force s'opposant à une deuxième force produite par cette pression dans le compartiment (28; 303) et compensant en particulier cette deuxième force.
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 true EP1082560A2 (fr) 2001-03-14
EP1082560B1 EP1082560B1 (fr) 2002-09-25

Family

ID=7869593

Family Applications (1)

Application Number Title Priority Date Filing Date
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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DE19816463C1 (de) 1998-04-14 1999-06-02 Siemens Ag Federbelastetes Tandem-Steuerventil
US6832628B2 (en) * 2000-10-11 2004-12-21 Flowmatrix, Inc. Variable pressure regulated flow controllers
US7621332B2 (en) * 2005-10-18 2009-11-24 Owen Oil Tools Lp Apparatus and method for perforating and fracturing a subterranean formation
DE102006049706B3 (de) * 2006-10-18 2008-06-19 Areva Np Gmbh Verfahren und eine Vorrichtung zur Prüfung der Funktionstüchtigkeit einer Steuereinheit mit einem Druck-Weg-Umformer und einem Sicherheitsventil
DE102007013359B4 (de) 2007-03-16 2013-04-04 Areva Np Gmbh Sicherheitseinrichtung zur Überdruckabsicherung eines druckführenden Systems
EP2335126A1 (fr) * 2008-10-14 2011-06-22 Circor Instrumentation Technologies, Inc. Procédé et appareil pour la commande de débit à faible puissance et/ou à haute pression
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
RU2766379C1 (ru) * 2021-07-12 2022-03-15 Артур Олегович Бурков Предохранительное устройство непрямого действия для гидросистем
CN117619320B (zh) * 2024-01-23 2024-04-30 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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CH675901A5 (fr) * 1988-10-13 1990-11-15 Sulzer Ag
DE3906888C2 (de) * 1989-03-03 1994-03-10 Siemens Ag Steuereinrichtung für ein Sicherheitsventil
DE19628610C1 (de) * 1996-07-16 1998-01-02 Siemens Ag Steuereinrichtung

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Title
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Also Published As

Publication number Publication date
US20010006078A1 (en) 2001-07-05
JP2002517680A (ja) 2002-06-18
WO1999063250A3 (fr) 2000-02-17
WO1999063250A2 (fr) 1999-12-09
RU2215223C2 (ru) 2003-10-27
DE19824494C1 (de) 1999-08-19
DE59902852D1 (de) 2002-10-31
US6386228B2 (en) 2002-05-14
JP3693917B2 (ja) 2005-09-14
EP1082560B1 (fr) 2002-09-25

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