EP0430089A1 - Actuateur - Google Patents

Actuateur Download PDF

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Publication number
EP0430089A1
EP0430089A1 EP90122361A EP90122361A EP0430089A1 EP 0430089 A1 EP0430089 A1 EP 0430089A1 EP 90122361 A EP90122361 A EP 90122361A EP 90122361 A EP90122361 A EP 90122361A EP 0430089 A1 EP0430089 A1 EP 0430089A1
Authority
EP
European Patent Office
Prior art keywords
valve
oil
plate
volume
actuator according
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
EP90122361A
Other languages
German (de)
English (en)
Other versions
EP0430089B1 (fr
Inventor
Heinz Frey
Kamil Prochazka
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.)
ABB Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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 ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0430089A1 publication Critical patent/EP0430089A1/fr
Application granted granted Critical
Publication of EP0430089B1 publication Critical patent/EP0430089B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/20—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted
    • F01D17/22—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical
    • F01D17/26—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical fluid, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/16—Trip gear
    • F01D21/18—Trip gear involving hydraulic means
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F15B2011/0243—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits the regenerative circuit being activated or deactivated automatically
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control

Definitions

  • the invention is based on an actuator for a control valve with a control circuit, which adjusts the actuator according to a setpoint specified by a higher-level system control system, with a main piston sliding in a master cylinder, with a drive volume which can be pressurized with oil under pressure on one side of the main piston and with an oil-filled buffer volume on the other side of the main piston.
  • An actuator for the actuation of a control valve with which, for example, the steam supply to a turbine of a power plant is regulated, has a main piston which is acted upon on the one hand by spring force and on the other hand by oil under pressure. When the oil pressure drops, the spring force securely closes the control valve, thereby interrupting the steam supply. This ensures that the turbine does not get out of control should the pressure of the oil fail.
  • the oil pressure in a drive volume which acts on the main piston and actuates the control valve via it, is generated by an electro-hydraulic converter. When the control valve moves in the opening direction, oil is fed into the drive volume under pressure, but since this movement takes place comparatively slowly, comparatively small cross sections are sufficient for the supply of the oil. A closing movement of the control valve must, however, be carried out at a speed which is about ten times higher. This requires a comparatively quick emptying of the drive volume, which however cannot be achieved due to the small cross-sections of the oil supply.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problem of creating an actuator for a control valve which, despite its higher performance, has a comparatively high dynamic which has a positive effect particularly when the control valve is closed.
  • FIG. 1 shows an actuator 1, which actuates a control valve 2, which regulates the amount of hot steam flowing through a hot steam line 3 to a turbine (not shown).
  • the control valve 2 is connected by a valve spindle 4 to a main piston 6 sliding in a master cylinder 5.
  • a drive volume 7 pressurized with oil is arranged below the main piston 6. Instead of the oil, another hydraulic fluid or a gaseous medium can also be provided.
  • An oil-filled buffer volume 8 is provided above the main piston 6, in which an additional one Spring 9 is arranged, which counteracts the oil pressure in the drive volume 7.
  • a rod 10 is provided on the spring side of the main piston 6 and connects it to a displacement measuring device 11.
  • the rod 10 and the valve stem 4 penetrate the master cylinder 5 on opposite sides. The structural design of these pressure-tight penetrations is known and need not be described further here.
  • a tubular connector 15 is attached to the master cylinder 5 in the area of the drive volume 7, the end 16 of which is remote from the master cylinder 5 is designed as a sealing seat. This end 16 is closed by a plate valve 17 shown in simplified form.
  • a plate 18 is pressed against the end 16 by a compression spring 19.
  • the compression spring 19 is arranged in a spring chamber 20 which is pressurized with oil.
  • the plate 18 In addition to the end 16 of the tubular connecting piece 15, the plate 18 simultaneously seals a volume 21 concentrically surrounding the connecting piece 15, which merges into a comparatively short, direct connecting line 22 which leads along the master cylinder 5 into the buffer volume 8.
  • This connecting line 22 has a comparatively large cross section.
  • the size of the spring chamber 20 is approximately 1,000 times smaller than the drive volume 7 with which it is in operative connection.
  • the spring chamber 20 is also operatively connected to a proportional directional valve 25.
  • a proportional directional control valve 25 for example, the directly operated proportional directional control valve with position control of the type KFDG 4V - 3/5, series 20, from Vickers Systems GmbH, D 6380 Bad Homburg vdH can be used.
  • the proportional directional control valve 25 has two actuating magnets 26, 27, which cooperate with return springs, not shown, and in this case three hydraulic connections 28, 29, 30.
  • the proportional directional control valve 25 is shown in the so-called "fail-safe" position.
  • the proportional directional valve 25 has a stroke measurement 31 connected to a slide of the valve, which measures the respective position of the slide and, as indicated by an action line 32, passes this information on to a position controller 33 with an integrated power amplifier.
  • a position amplifier 33 for example, can be a power amplifier EEA-PAM-533-A, series 20, specially matched to the proportional control valve 25, from Vickers Systems GmbH, D 6380 Bad Homburg vdH.
  • This position controller 33 works together with a higher-order controller 36, as indicated by an action line 37.
  • the controller 36 has further inputs 38, through which information and commands are fed in by a higher-level plant control system that controls the entire power plant. Furthermore, it has an input 39 for feeding in an electrical signal, as indicated by an action line 40, from the displacement measuring device 11.
  • Oil is fed in under pressure through a line 45, and the necessary oil pressure is generated by a pump (not shown).
  • the flow rate of the oil is limited to a maximum amount by an orifice 46 arranged in the line 45.
  • This aperture 46 can have a constant or an adjustable cross section.
  • the line 45 leads to the connection 28 of the proportional directional control valve 25, which in the illustration in FIG. 1 is not connected through to the connection 29.
  • the connection 29 is connected on the one hand to a line 47 which leads into the spring chamber 20 of the plate valve 17, and on the other hand with a line 48 which leads to a normally closed safety valve 49 designed as a plate valve. After the safety valve 49, a line 50 leads into the buffer volume of the master cylinder 5.
  • a line 51 branches off from the line 50 and establishes the connection with the connection 30 of the proportional directional valve 25.
  • a line 52 leads from the buffer volume 8 to a drain device, not shown. From this drain device, the oil continues through the aforementioned pump back into line 45.
  • the safety valve 49 is designed as a plate valve with a cylinder 53, a volume 55 which is pressurized with oil under pressure from a safety oil circuit through a line 54 and which is delimited by a valve plate 56 and with a valve spring 57 which controls the oil pressure acting on the valve plate 56 counteracts. It cannot be seen from the schematic illustration of the safety valve 49 that the valve plate 56 is designed in such a way that it is impossible to jam it.
  • the line 54 normally leads through a directional valve 58.
  • the directional control valve 58 is actuated by an electromagnet 59.
  • a line of action 60 indicates the path of the trigger command for the electromagnet 59. For safety reasons, this trigger command is usually locked with the higher-level system control system, so that no unwanted false triggers can occur.
  • a line 61 which branches off from line 45, leads to directional control valve 58. Via this line, if e.g. the safety oil circuit is depressurized, the oil pressure from line 45 after switching directional control valve 58, apply volume 55 and keep safety valve 49 closed.
  • the proportional directional valve 25 is connected to the plate valve 17 and the master cylinder 5 to form a monolithic unit.
  • the lines 47 and 48 like the lines 50 and 51, can be made comparatively short, so that the oil-filled line volumes are correspondingly small, which increases the dynamics.
  • the actuator is therefore very versatile.
  • the interaction of the position controller 33 with the integrated power amplifier and the controller 36 as a common electronic control arrangement of a control circuit is particularly advantageous because the position controller 33 is specially adapted to the proportional directional control valve 25, so that no additional adjustments and adjustments are necessary.
  • this electronic control system it is entirely possible to assemble this electronic control system from other elements or to transfer its function to a higher-level system control system if, for example, the protection concept of the power plant system would require this.
  • signals originating from the displacement measuring device 11 and from the stroke measurement 31 are processed continuously together with at least one setpoint value specified by the higher-level system control system according to a specified logic. In the event of deviations from this target value, this control arrangement generates correction signals which act on the actuating magnets 26, 27 of the proportional directional control valve 25 and cause the same to be reversed accordingly.
  • a breakthrough through the plate 18 has a cylindrical opening 66, which is followed by a conical extension.
  • a ball 67 is pressed into this conical extension by a spring 68, which is supported against a holder 69 connected to the plate 18, and closes the opening 66.
  • Oil 66 can flow under pressure into the drive volume 7 as soon as one Pressure difference occurs that is large enough to overcome the force of the spring 68 and the oil pressure acting on the ball 67.
  • FIG. 3 is similar to FIG. 2, except that in this case an opening with the opening 66 through the plate 18 is designed in such a way that oil can flow from the drive volume 7 into the spring chamber 20.
  • the cross section of the diaphragm 70 is designed to be significantly smaller than that of the opening 66.
  • FIG. 5 shows a plate 18 with two valve arrangements similar to that shown in FIG. 2, but which allow oil to pass through in opposite directions with a corresponding differential pressure.
  • the opening 66 which leads from the drive volume 7 into the spring chamber 20, has a substantially larger cross section than the second opening 66.
  • FIG. 1 is considered in more detail.
  • the control valve 2 must be able to be closed comparatively quickly during operation.
  • the closing speed is normally around 1 m / sec, while the opening speed, on the other hand, only requires speeds around 0.02 m / sec.
  • These speed specifications are guide values; depending on the design of the power plant, significant deviations from these specifications can also occur.
  • the actuator 1 can be adapted to the respective operating conditions with comparatively little effort.
  • the proportional directional control valve 25 is actuated by the position controller 33, and it is controlled in such a way that the scheme to the left of the position shown applies.
  • the connections 28 and 29 are then connected through and oil under pressure flows from the line 45 through the proportional directional control valve 25. No oil can flow through line 48 in normal operation, since the safety valve 49 closes this line 48.
  • the oil flows through the line 47 into the spring chamber 20 of the plate valve 17 and from there through the opening of the plate 18 and the connector 15 into the drive volume 7.
  • the oil pressure in the drive volume 7 moves the main piston 6 upwards and thus via the valve spindle 4 the control valve 2 in the opening direction.
  • the displacement measuring device 11 monitors the stroke of the main piston 6 and reports its position continuously to the controller 36. As soon as the predetermined setpoint value of the stroke has been reached, the controller 36 controls the proportional directional control valve 25 via the position controller 33 so that the oil flow is interrupted.
  • the proportional directional control valve 25 is reversed such that the scheme to the right of the position shown applies.
  • the connections 29 and 30 are connected to one another and oil from the spring chamber 20 flows out through the line 47, through the proportional directional control valve 25, through the lines 51 and 50 further through the buffer volume 8 and the line 52 into the drain device.
  • this flow process takes only a very short time because, as soon as the pressure in the spring chamber 20 is less than the pressure in the drive volume 7, the plate 18 moves to the right against the pressure of the spring 19 and the oil from the drive volume 7 through the volume 21 and the connecting line 22 can flow into the buffer volume 8 filled with oil under low pressure and from there further into the drain device.
  • the spring 9 pushes the main piston 6 down and thus the oil from the drive volume 7 into the buffer volume 8 until the end position of the control valve 2 is reached.
  • the oil flows out very quickly, since the cross-section released by the plate valve 17 and also the cross-section of the direct connecting line 22 are comparatively large and do not negatively influence the flow process.
  • the movement of the main piston 6 creates a suction in the buffer volume 8, which additionally supports this oil flow and increases the dynamics of the actuator 1.
  • the closing movement of the control valve is initiated by lowering the oil pressure in the spring chamber 20, whereupon, if only a small stroke has to be made in the closing direction, the plate valve 17 only for a short time opens and oil can escape through the connecting line 22 into the buffer volume 8. As soon as the desired value is reached, the plate valve 17 closes again immediately.
  • the design of the plate 18 according to FIG. 5 also allows a small closing movement, for larger strokes of the main piston 6 it is also necessary to open the plate valve 17 in this case.
  • the proportional directional control valve 25 is shown in the central position in FIG. 1. This position is assumed if, for example, the actuating magnets 26, 27 should not receive any voltage due to a power failure. Reaching this position is ensured by the spring force of springs provided in the interior of the proportional directional valve 25 under all circumstances. In this position, the spring chamber 20 is relieved of pressure by the lines 47, 51 and 50, so that the plate valve 17 opens, which, as already described, leads to a rapid closing of the control valve 2. In this way it is ensured that the control valve 2 is always definitely closed even in the event of a fault, so that under no circumstances can damage to the operated turbine occur as a result of a defect in the actuator 1.
  • the safety valve 49 normally prevents a pressure drop in the line 48 in the direction of the drain device. However, if the pressure in the safety oil circuit drops, the pressure in the volume 55 also drops and the safety valve 49 releases the line 48, regardless of the position of the proportional directional control valve 25, so that the pressure can escape from the spring chamber 20 of the plate valve 17 the lines 47, 48 and 50, whereby, as already described, a quick closing process of the control valve 2 is initiated. This measure can also be used to reliably shut off the steam supply to the turbine.
  • the directional control valve 58 is installed, which, as soon as it is switched electromagnetically to the diagram shown on the right of the position shown, enables oil to act on the volume 55 under pressure from the line 45 through the line 61 and through the directional control valve 58 can, whereby the safety valve 49 is closed.
  • the command route for the directional control valve 58 as indicated by the line of action 60, must however be blocked as soon as it is switched over to normal operation, since otherwise the safety oil circuit may no longer be able to act on the safety valve 49, so that the protective function of this circuit can no longer be guaranteed would.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
EP90122361A 1989-12-01 1990-11-23 Actuateur Expired - Lifetime EP0430089B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH431589 1989-12-01
CH4315/89 1989-12-01

Publications (2)

Publication Number Publication Date
EP0430089A1 true EP0430089A1 (fr) 1991-06-05
EP0430089B1 EP0430089B1 (fr) 1994-03-02

Family

ID=4273790

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90122361A Expired - Lifetime EP0430089B1 (fr) 1989-12-01 1990-11-23 Actuateur

Country Status (4)

Country Link
US (1) US5137253A (fr)
EP (1) EP0430089B1 (fr)
DE (1) DE59004774D1 (fr)
ES (1) ES2052136T3 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0540963A1 (fr) * 1991-11-04 1993-05-12 Asea Brown Boveri Ag Système d'alimentation pour système hydraulique divisé
DE4244304A1 (de) * 1992-12-28 1994-06-30 Asea Brown Boveri Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal
EP0631056A1 (fr) * 1993-06-24 1994-12-28 ABB Management AG Dispositif d'entraînement pour une vanne de réglage
WO1995012057A1 (fr) * 1993-10-29 1995-05-04 Siemens Aktiengesellschaft Moteur de commande, notamment pour soupapes a fermeture rapide
AT410361B (de) * 1997-11-05 2003-04-25 Techno Alpin Gmbh S R L Motorischer stellantrieb
CN109404065A (zh) * 2018-10-12 2019-03-01 上海华电电力发展有限公司 防止主机汽门遮断电磁阀故障引起机组跳闸的控制方法

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014226666B3 (de) 2014-12-19 2015-12-24 Voith Patent Gmbh Stellantrieb für ein Regelventil, insbesondere Dampfturbinenregelventil und Verfahren zum Betreiben desselben
EP3445978B1 (fr) * 2016-04-19 2021-03-10 Clearmotion, Inc. Procédés et systèmes actifs de suppression des ondulations hydrauliques
DE102017131004A1 (de) * 2017-12-21 2019-06-27 Moog Gmbh Stellantrieb mit hydraulischem Abflussverstärker
JP7297617B2 (ja) * 2019-09-13 2023-06-26 日本ムーグ株式会社 電動油圧アクチュエータシステム、電動油圧アクチュエータシステムの油圧回路、及びそれを含む蒸気タービンシステム

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE285195C (fr) * 1914-05-13
DE519057C (de) * 1929-02-16 1931-02-23 Siemens Schuckertwerke Akt Ges Steuerung der Hilfsoelpumpe einer Dampfturbine
FR1156683A (fr) * 1955-10-17 1958-05-20 Licentia Gmbh Soupape de démarrage et à fermeture instantanée actionnée hydrauliquement, notamment pour turbines à gaz et à vapeur
DE1257158B (de) * 1956-10-22 1967-12-28 Gen Electric Hydraulische Regeleinrichtung fuer eine Dampfturbine mit Zwischenueberhitzung
US3495501A (en) * 1968-06-04 1970-02-17 Gen Electric Valve operating and emergency closing mechanism
EP0127027A1 (fr) * 1983-05-30 1984-12-05 BBC Brown Boveri AG Servomoteur électrohydraulique pour soupapes de turbines
DE3432890A1 (de) * 1984-07-20 1986-01-23 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau Einrichtung zur ueberwachung von physikalischen groessen an anlagen

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE372055B (fr) * 1973-03-23 1974-12-09 Stal Laval Turbin Ab
US4043533A (en) * 1975-08-14 1977-08-23 Atwood & Morrill Co. Auxiliary closing force for valves
US4149565A (en) * 1977-02-02 1979-04-17 International Harvester Company Pilot controlled poppet valve assembly
US4335867A (en) * 1977-10-06 1982-06-22 Bihlmaier John A Pneumatic-hydraulic actuator system
DE2835771A1 (de) * 1978-08-16 1980-02-28 Schwelm & Towler Hydraulics Anordnung zur aussteuerung eines cartridgeelementes
US4215844A (en) * 1978-08-28 1980-08-05 The Babcock & Wilcox Company Valve actuator system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE285195C (fr) * 1914-05-13
DE519057C (de) * 1929-02-16 1931-02-23 Siemens Schuckertwerke Akt Ges Steuerung der Hilfsoelpumpe einer Dampfturbine
FR1156683A (fr) * 1955-10-17 1958-05-20 Licentia Gmbh Soupape de démarrage et à fermeture instantanée actionnée hydrauliquement, notamment pour turbines à gaz et à vapeur
DE1257158B (de) * 1956-10-22 1967-12-28 Gen Electric Hydraulische Regeleinrichtung fuer eine Dampfturbine mit Zwischenueberhitzung
US3495501A (en) * 1968-06-04 1970-02-17 Gen Electric Valve operating and emergency closing mechanism
EP0127027A1 (fr) * 1983-05-30 1984-12-05 BBC Brown Boveri AG Servomoteur électrohydraulique pour soupapes de turbines
DE3432890A1 (de) * 1984-07-20 1986-01-23 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau Einrichtung zur ueberwachung von physikalischen groessen an anlagen

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0540963A1 (fr) * 1991-11-04 1993-05-12 Asea Brown Boveri Ag Système d'alimentation pour système hydraulique divisé
US5280807A (en) * 1991-11-04 1994-01-25 Asea Brown Boveri Ltd. Supply circuit for a two-tube hydraulic system
DE4244304A1 (de) * 1992-12-28 1994-06-30 Asea Brown Boveri Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal
EP0604805A1 (fr) * 1992-12-28 1994-07-06 Asea Brown Boveri Ag Dispositif de commande pour vérin hydraulique avec signal de réglage proportionnel
US5435227A (en) * 1992-12-28 1995-07-25 Asea Brown Boveri Ag Operating mechanism for a hydraulic actuator having a pressure-proportional actuating signal
EP0631056A1 (fr) * 1993-06-24 1994-12-28 ABB Management AG Dispositif d'entraînement pour une vanne de réglage
DE4320937A1 (de) * 1993-06-24 1995-01-05 Abb Management Ag Stellantrieb für ein Regelventil
US5467683A (en) * 1993-06-24 1995-11-21 Abb Management Ag Actuating drive for a control valve
WO1995012057A1 (fr) * 1993-10-29 1995-05-04 Siemens Aktiengesellschaft Moteur de commande, notamment pour soupapes a fermeture rapide
AT410361B (de) * 1997-11-05 2003-04-25 Techno Alpin Gmbh S R L Motorischer stellantrieb
CN109404065A (zh) * 2018-10-12 2019-03-01 上海华电电力发展有限公司 防止主机汽门遮断电磁阀故障引起机组跳闸的控制方法

Also Published As

Publication number Publication date
EP0430089B1 (fr) 1994-03-02
US5137253A (en) 1992-08-11
DE59004774D1 (de) 1994-04-07
ES2052136T3 (es) 1994-07-01

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