EP0451543A1 - Actuation system for a steam regulating valve - Google Patents

Actuation system for a steam regulating valve Download PDF

Info

Publication number
EP0451543A1
EP0451543A1 EP91104112A EP91104112A EP0451543A1 EP 0451543 A1 EP0451543 A1 EP 0451543A1 EP 91104112 A EP91104112 A EP 91104112A EP 91104112 A EP91104112 A EP 91104112A EP 0451543 A1 EP0451543 A1 EP 0451543A1
Authority
EP
European Patent Office
Prior art keywords
control
valve
control valve
drive according
control valves
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
EP91104112A
Other languages
German (de)
French (fr)
Other versions
EP0451543B1 (en
Inventor
Edi Burch
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=4204939&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0451543(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0451543A1 publication Critical patent/EP0451543A1/en
Application granted granted Critical
Publication of EP0451543B1 publication Critical patent/EP0451543B1/en
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

Links

Images

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
    • 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

Definitions

  • the present invention is based on a drive for a steam control valve according to the preamble of patent claim 1.
  • a drive for a steam control valve is known with a control valve arrangement which regulates the pressure of the oil for the hydraulic actuation of an actuator.
  • This control valve arrangement has a slide valve with sealing edges.
  • slide valves are only suitable to a limited extent, since oil resin and particle contamination can impair their function.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problem of creating a drive for a steam control valve which can always be actuated safely and quickly even with a comparatively high oil pressure.
  • Fig. 1 shows a schematic representation of an actuator 1 for a steam control valve 2, which controls the amount of hot steam flowing through a hot steam line 3 to a turbine, not shown.
  • the steam control valve 2 is through a valve spindle 4 with a in a master cylinder 5 sliding main piston 6 connected.
  • a drive volume 7 pressurized with oil is arranged below the main piston 6.
  • another fluid or a gaseous medium can also be provided.
  • the use of water or water emulsions is also possible.
  • An oil-filled buffer volume 8 is provided above the main piston 6, in which a spring 9 is also 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 spindle 4 penetrate the master cylinder 5 on opposite sides, the instruction of these pressure-tight penetrations being assumed to be known.
  • Oil is fed in under pressure through a line 13, and the necessary oil pressure is generated by a pump (not shown).
  • the line 13 leads through an orifice 14 provided for the opening time limitation of the actuator 1 to an inlet 16 of a first control valve 17 designed as a control valve.
  • a line 15 feeds oil under pressure from a safety oil circuit.
  • a line 18 branches off from line 15, which has an orifice 19 and opens into a drive volume 20 of a second control valve 21 designed as a control valve.
  • the line 15 also has an orifice 26 and leads into a drive volume 27 of the first control valve 17. Between the orifice 26 and the drive volume 27, a line 28 branches off from the line 15 and leads into a first proportional pressure valve 29 designed as a seat valve leads.
  • An outlet 30 of this proportional pressure valve 29 is connected to a line 31 which, on the one hand, is connected to the buffer volume 8 and, on the other hand, is connected to a drain device (not shown) via a check valve 32.
  • the check valve 32 prevents oil pressure surges, which possibly get into the drain device, from interfering with the actuator 1 through the line 31. From this drain device the oil continues through the aforementioned pump back into line 13.
  • a line 33 branches off from line 18 and leads into a second proportional pressure valve 34 designed as a seat valve.
  • An output 35 of this proportional pressure valve 34 is connected to the line 31.
  • the first control valve 17 is shown in the closed state in FIG. 1, specifically a seat valve 40 prevents the inlet 16 from being connected through to an outlet 41.
  • the input 16 is connected to a drive volume 44 via a line 43.
  • a pressure building up in this drive volume 44 acts in the same direction as the force of a spring 42, that is to say counter to the pressure prevailing in the drive volume 27.
  • the piston area belonging to the drive volume 44 is smaller than that of the piston belonging to the drive volume 27, so that it is ensured that the control valve 17 can always be actuated solely by the pressure of the safety oil.
  • the first control valve 17 has three schematically illustrated switching positions, of which the uppermost, the blocking position, has already been described, the middle position shows a passage position with a controllable cross section and the bottom one shows a passage position with a constant cross section.
  • the control valve 17 is actuated by oil pressure in the drive volume 27, i.e. as the oil pressure rises, it is pressed from the blocking position through the open position with adjustable cross section to the open position with constant cross section.
  • the pressure in the drive volume 44 and the force of the spring 42 work against this oil pressure in the drive volume 27.
  • the outlet 41 is connected via a line 46 to a connection 47 which establishes a connection with the drive volume 7 of the actuator 1. In addition, this connection is 47 connected to an input 48 of the second control valve 21.
  • the second control valve 21 has three schematically illustrated switching positions, the uppermost of which acts as a passage position with a constant cross section.
  • the middle switching position acts as an open position with an adjustable cross-section and the lowest as a blocking position.
  • the control valve 21 is actuated by oil pressure in the drive volume 20, ie with increasing oil pressure, it is pressed from the open position with a constant cross section through the open position with a controllable cross section into the blocking position.
  • the force of a spring 51 works against this oil pressure in the drive volume 20.
  • the blocking position is realized by a seat valve 52.
  • the input 48 is also connected to a drive volume 54 via a line 53.
  • a pressure building up in this drive volume 54 acts in the same direction as the force of the spring 51, that is to say counter to the pressure prevailing in the drive volume 20.
  • the piston area belonging to the drive volume 54 is smaller than that of the piston belonging to the drive volume 20, so that it is ensured that the control valve 21 can always be actuated solely by the pressure of the safety oil.
  • the two control valves 17 and 21 each have a passage position with an adjustable cross section, each with a specific control characteristic. This control characteristic can now be configured identically in both control valves 17, 21, the cross sections to be controlled being configured differently.
  • control characteristic it is also possible for this control characteristic to be designed differently in each of the two control valves 17, 21. These different control characteristics make it possible to optimally adapt the control valves 17, 21 to one another and to the respective operating requirements, so that the drive can be used in a comparatively large area of application. Any necessary adjustments to extended operating requirements can be made comparatively easily carry out, since only the geometry in the area of the adjustable cross-section needs to be changed.
  • the first proportional pressure valve 29 acts similarly to an adjustable orifice, in which on the one hand the orifice opening is to be enlarged via a line 55 with the aid of the oil pressure present, while on the other hand an electromagnet 56, working against this oil pressure, wants to reduce the orifice opening.
  • a line of action 57 indicates that the electromagnet 56 is selectively actuated by an electronic control arrangement 58.
  • the second proportional control valve 34 also acts, in which the oil pressure acts via a line 59 in the opening direction and an electromagnet 60 in the closing direction.
  • a line of action 61 indicates that the electromagnet 60 is also selectively actuated by the electronic control arrangement 58.
  • the electronic control arrangement 58 is also, as indicated by an action line 62, in operative connection with the displacement measuring device 11.
  • An action line 63 indicates that commands and signals of a higher-level system control system are also entered into the electronic control arrangement 58 and implemented therein.
  • the two proportional pressure valves 29 and 34 are designed as seat valves, so that any decomposition or resinification of the oil cannot impair the function of these valves. Due to the seat construction, a comparatively high level of safety and availability of these valves is achieved. However, it is also possible to use servo valves at these points in the arrangement.
  • the embodiment according to FIG. 2 corresponds almost completely to the embodiment shown in FIG. 1, only the control valves 17 and 21 are each additionally provided with a displacement measuring device 65 and 66.
  • the signals emitted by the displacement measuring device 65 become, as by an action line 67 indicated, fed into the electronic control arrangement 58 and further implemented there.
  • the signals emitted by the displacement measuring device 66 are, as indicated by an action line 68, fed into the electronic control arrangement 58 and further processed there.
  • the embodiment according to FIG. 3 has only a single proportional pressure valve 29 compared to the embodiment according to FIG. 1, which is pressurized with oil via the line 15 and the orifice 26.
  • the drive volume 27 of the control valve 17 is pressurized with this oil.
  • a line 67 branches off from line 15 between orifice 26 and drive volume 27. This line 67 opens directly into the drive volume 20 of the control valve 21.
  • the drive volumes 27 and 20 are therefore acted upon in parallel and simultaneously with the oil fed in from the line 15 under pressure.
  • the springs 42 and 51 of the two control valves 17 and 21 counteracting this oil under pressure are mounted in such a way that their pretensioning force can be adjusted mechanically. This adjustability is symbolized by arrows.
  • FIG. 1 shows the drive in the fail-save position, in which, for example, the line 15 is without pressure and in which the steam control valve 2 is closed.
  • both the line 13 and the line 15 can be pressurized, and for the steam control valve 2 to be closed solely by electrically deactivating the proportional pressure valves 29 and 34.
  • the electromagnets 56 and 60 are controlled such that the oil pressure present through the lines 55 and 59 sets the proportional pressure valves 29 and 34 to passage, so that no oil pressure can build up in the drive volumes 20 and 27.
  • the control valves 17 and 21 are not actuated, so that their 1 position is maintained and the steam control valve 2 remains closed.
  • the path measuring device 11 delivers path-dependent signals into the electronic control arrangement 58, where they are evaluated and compared with a predetermined target value. This setpoint is specified by a higher-level system control system. In accordance with the result of this target / actual comparison, the excitation of the electromagnets 56 and 60 is changed by the electronic control arrangement 58, as a result of which the position of the controllable control valves 17 and 21 is also changed accordingly.
  • the orifice 14 limits the opening time of the actuator 1, so that in the actuator 1 about fast moving and braking masses no mechanical defects can occur. Furthermore, this opening time limitation has a positive effect on the operating behavior of the turbine, which is not subjected to sudden loads with hot steam.
  • the main piston 6 is pressed upward by the oil fed into the drive volume 7, at the same time the oil in the buffer volume 8 flows through the line 31 into the outlet.
  • the opening movement of the actuator 1 is comparatively slow, but the closing must be done very quickly for safety reasons.
  • the oil flows from the drive volume 7 through the control valve 21, the line 50 and the upper part of the line 31 directly into the buffer volume 8. In this way, the oil can be discharged in the shortest possible way and thus very quickly to remove the drive volume 7, whereby an advantageously high dynamic of the actuator 1 is achieved in the closing direction.
  • the embodiment according to FIG. 2 enables an even more sensitive and rapid approximation to the predetermined setpoint, since the signals from the path measuring devices 65, 66 are additionally processed in the electronic control arrangement 58, which enables the setpoint of the drive position to be reached more quickly and more precisely.
  • the mode of operation of this arrangement is otherwise the same as for the arrangement according to FIG. 1.
  • the embodiment according to FIG. 3 also works similarly to the embodiment according to FIG. 1.
  • the pressure build-up in the drive volumes 27 and 20 is achieved here with the aid of only one proportional pressure valve 29, so that both drive volumes 27 and 20 are pressurized simultaneously and identically will.
  • Any settings for the response behavior of the control valves 17 and 21 can be made here when the system is started up using the adjustable preload force of the springs 42 and 51 are carried out, so that here, despite identical pressurization, the respective operating tasks of the control valves 17 and 21 can be set to different response times.
  • this simplified embodiment can cover a comparatively large range of requirements in an economically justifiable manner.
  • this drive for a steam control valve 2 is suitable for actuation by high oil pressures, namely pressures of up to 200 bar and higher are possible.
  • high oil pressures namely pressures of up to 200 bar and higher are possible.
  • These high pressures do not negatively influence the operational safety and the availability of the drive, since seat valves are provided at all sealing points where these high pressures occur, the operating behavior of which is not impaired by any oil resinification, in particular these are the proportional pressure valves 29 and 34 and the seat valves 40 and 52 of the control valves 17 and 21.
  • the dynamic gain of the arrangement achieved by the high actuation pressure can therefore be used advantageously and in full to improve the control behavior of the arrangement.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)
  • Fluid-Driven Valves (AREA)
  • Temperature-Responsive Valves (AREA)
  • Servomotors (AREA)

Abstract

This actuating system for a steam regulating valve (2) has a control valve arrangement for controlling the operating pressure of an actuating system (1). <??>It is intended to create an actuating system for a steam regulating valve which can always be operated safely and quickly even with a comparatively high oil pressure. This is achieved in that the control valve arrangement has at least two controllable control valves (17, 21) which are pressure-operated via at least one servo control valve (proportional pressure valve 29, 34). <IMAGE>

Description

TECHNISCHES GEBIETTECHNICAL AREA

Die vorliegende Erfindung geht aus von einem Antrieb für ein Dampfstellventil gemäss dem Oberbegriff des Patentanspruchs 1.The present invention is based on a drive for a steam control valve according to the preamble of patent claim 1.

STAND DER TECHNIKSTATE OF THE ART

Aus der Offenlegungsschrift DE 35 35 174 ist ein Antrieb für ein Dampfstellventil bekannt mit einer Steuerventilanordnung, welche den Druck des Öls für die hydraulische Betätigung eines Stellantriebs regelt. Diese Steuerventilanordnung weist ein Schieberventil mit Dichtkanten auf. Für Öldrücke oberhalb etwa 40 bar sind Schieberventile nur bedingt geeignet, da Ölverharzungen und Partikelverschmutzungen deren Funktion beeinträchtigen können.From the published patent application DE 35 35 174, a drive for a steam control valve is known with a control valve arrangement which regulates the pressure of the oil for the hydraulic actuation of an actuator. This control valve arrangement has a slide valve with sealing edges. For oil pressures above about 40 bar, slide valves are only suitable to a limited extent, since oil resin and particle contamination can impair their function.

DARSTELLUNG DER ERFINDUNGPRESENTATION OF THE INVENTION

Hier will die Erfindung Abhilfe schaffen. Die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, löst die Aufgabe, einen Antrieb für ein Dampfstellventil zu schaffen, welcher auch mit vergleichsweise hohem Öldruck stets sicher und schnell betätigt werden kann.The invention seeks to remedy this. The invention, as characterized in the claims, solves the problem of creating a drive for a steam control valve which can always be actuated safely and quickly even with a comparatively high oil pressure.

Die durch die Erfindung erreichten Vorteile sind im wesentlichen darin zu sehen, dass die mit höheren Öldrücken erreichbare bessere Dynamik des Antriebs nun voll ausgenutzt werden kann. Eine Verharzung der Steuerventilanordnung und eine damit verbundene Beeinträchtigung der Betriebssicherheit des Stellantriebs kann mit grosser Sicherheit ausgeschlossen werden. Zudem erweist es sich als vorteilhaft, dass vergleichsweise einfach gebaute Ventile eingesetzt werden können, was die Wirtschaftlichkeit des Antriebs erhöht.The advantages achieved by the invention can essentially be seen in the fact that the better dynamics of the drive that can be achieved with higher oil pressures can now be fully utilized. Resinification of the control valve arrangement and an associated impairment of the operational safety of the actuator can be excluded with great certainty. In addition, it proves advantageous that comparatively simple valves can be used, which increases the efficiency of the drive.

Die weiteren Ausgestaltungen der Erfindung sind Gegenstände der abhängigen Ansprüche.The further developments of the invention are the subject of the dependent claims.

Die Erfindung, ihre Weiterbildung und die damit erzielbaren Vorteile werden nachstehend anhand der Zeichnung, welche lediglich einen Ausführungsweg darstellt, näher erläutert.The invention, its further development and the advantages which can be achieved thereby are explained in more detail below with reference to the drawing, which only represents one embodiment.

KURZE BESCHREIBUNG DER ZEICHNUNGBRIEF DESCRIPTION OF THE DRAWING

Es zeigen:

  • Fig. 1 eine erste Ausführungsform des Antriebs,
  • Fig. 2 eine zweite Ausführungsform des Antriebs und
  • Fig. 3 eine dritte Ausführungsform des Antriebs.
Show it:
  • 1 shows a first embodiment of the drive,
  • Fig. 2 shows a second embodiment of the drive and
  • Fig. 3 shows a third embodiment of the drive.

Bei allen Figuren sind gleich wirkende Elemente mit gleichen Bezugszeichen versehen.Elements with the same effect are provided with the same reference symbols in all the figures.

WEGE ZUR AUSFÜHRUNG DER ERFINDUNGWAYS OF CARRYING OUT THE INVENTION

Fig. 1 zeigt in schematischer Darstellung einen Stellantrieb 1 für ein Dampfstellventil 2, welches die durch eine Heissdampfleitung 3 zu einer nicht dargestellten Turbine strömende Heissdampfmenge regelt. Das Dampfstellventil 2 ist durch eine Ventilspindel 4 mit einem in einem Hauptzylinder 5 gleitenden Hauptkolben 6 verbunden. Unterhalb des Hauptkolbens 6 ist ein mit Öl unter Druck beaufschlagtes Antriebsvolumen 7 angeordnet. Anstelle des Öls kann auch eine anderes Fluid oder ein gasförmiges Medium vorgesehen werden. Insbesondere ist auch der Einsatz von Wasser oder Wasseremulsionen möglich. Oberhalb des Hauptkolbens 6 ist ein ölgefülltes Puffervolumen 8 vorgesehen, in welchem zudem eine Feder 9 angeordnet ist, welche dem Öldruck im Antriebsvolumen 7 entgegenwirkt. Am Hauptkolben 6 ist federseitig eine Stange 10 vorgesehen, welche denselben mit einer Wegmesseinrichtung 11 verbindet. Die Stange 10 und die Ventilspindel 4 durchdringen den Hauptzylinder 5 an entgegengesetzten Seiten, wobei die Instruktion dieser druckdicht ausgeführten Durchdringungen als bekannt vorausgesetzt wird.Fig. 1 shows a schematic representation of an actuator 1 for a steam control valve 2, which controls the amount of hot steam flowing through a hot steam line 3 to a turbine, not shown. The steam control valve 2 is through a valve spindle 4 with a in a master cylinder 5 sliding main piston 6 connected. A drive volume 7 pressurized with oil is arranged below the main piston 6. Instead of the oil, another fluid or a gaseous medium can also be provided. In particular, the use of water or water emulsions is also possible. An oil-filled buffer volume 8 is provided above the main piston 6, in which a spring 9 is also 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 spindle 4 penetrate the master cylinder 5 on opposite sides, the instruction of these pressure-tight penetrations being assumed to be known.

Durch eine Leitung 13 wird Öl unter Druck eingespeist, der nötige Öldruck wird durch eine nicht dargestellte Pumpe erzeugt. Die Leitung 13 führt durch eine für die Öffnungszeitbegrenzung des Stellantriebs 1 vorgesehene Blende 14 zu einem Eingang 16 eines ersten als Regelventil ausgebildeten Steuerventils 17. Durch eine Leitung 15 wird von einem Sicherheitsölkreislauf her Öl unter Druck eingespeist. Von der Leitung 15 zweigt eine Leitung 18 ab, die eine Blende 19 aufweist und die in ein Antriebsvolumen 20 eines zweiten als Regelventil ausgebildeten Steuerventils 21 mündet. Die Leitung 15 weist zudem eine Blende 26 auf und führt in ein Antriebsvolumen 27 des ersten Steuerventils 17. Zwischen der Blende 26 und dem Antriebsvolumen 27 zweigt von der Leitung 15 eine Leitung 28 ab, die in ein erstes, als Sitzventil ausgebildetes Proportional-Druckventil 29 führt. Ein Ausgang 30 dieses Proportional-Druckventils 29 ist mit einer Leitung 31 verbunden, die einerseits mit dem Puffervolumen 8 und andererseits über ein Rückschlagventil 32 mit einer nicht dargestellten Ablaufvorrichtung in Verbindung steht. Das Rückschlagventil 32 verhindert, dass Öldruckstösse, die eventuell in die Ablaufvorrichtung gelangen, durch die Leitung 31 störend auf den Stellantrieb 1 zurückwirken können. Von dieser Ablaufvorrichtung gelangt das Öl weiter durch die erwähnte Pumpe zurück in die Leitung 13. Zwischen der Blende 19 und dem Antriebsvolumen 20 zweigt von der Leitung 18 eine Leitung 33 ab, die in ein zweites als Sitzventil ausgebildetes Proportional-Druckventil 34 führt. Ein Ausgang 35 dieses Proportional-Druckventils 34 ist mit der Leitung 31 verbunden.Oil is fed in under pressure through a line 13, and the necessary oil pressure is generated by a pump (not shown). The line 13 leads through an orifice 14 provided for the opening time limitation of the actuator 1 to an inlet 16 of a first control valve 17 designed as a control valve. A line 15 feeds oil under pressure from a safety oil circuit. A line 18 branches off from line 15, which has an orifice 19 and opens into a drive volume 20 of a second control valve 21 designed as a control valve. The line 15 also has an orifice 26 and leads into a drive volume 27 of the first control valve 17. Between the orifice 26 and the drive volume 27, a line 28 branches off from the line 15 and leads into a first proportional pressure valve 29 designed as a seat valve leads. An outlet 30 of this proportional pressure valve 29 is connected to a line 31 which, on the one hand, is connected to the buffer volume 8 and, on the other hand, is connected to a drain device (not shown) via a check valve 32. The check valve 32 prevents oil pressure surges, which possibly get into the drain device, from interfering with the actuator 1 through the line 31. From this drain device the oil continues through the aforementioned pump back into line 13. Between the orifice 19 and the drive volume 20, a line 33 branches off from line 18 and leads into a second proportional pressure valve 34 designed as a seat valve. An output 35 of this proportional pressure valve 34 is connected to the line 31.

Das erste Steuerventil 17 ist in der Fig. 1 in geschlossenem Zustand dargestellt, und zwar verhindert ein Sitzventil 40, dass der Eingang 16 zu einem Ausgang 41 durchverbunden wird. Der Eingang 16 ist über eine Leitung 43 mit einem Antriebsvolumen 44 verbunden. Ein sich in diesem Antriebsvolumen 44 aufbauender Druck wirkt in die gleiche Richtung wie die Kraft einer Feder 42, also entgegen dem im Antriebsvolumen 27 herrschenden Druck. In der Regel ist jedoch die zum Antriebsvolumen 44 zugehörige Kolbenfläche kleiner als die des zum Antriebsvolumen 27 gehörenden Kolbens, sodass sichergestellt ist, dass das Steuerventil 17 stets allein durch den Druck des Sicherheitsöls betätigt werden kann. Das erste Steuerventil 17 weist drei schematisch dargestellte Schaltstellungen auf, von denen die oberste, die Sperrstellung, bereits beschrieben wurde, die mittlere Stellung zeigt eine Durchlassstellung mit regelbarem Querschnitt und die unterste zeigt eine Durchlassstellung mit konstantem Querschnitt. Das Steuerventil 17 wird durch Öldruck im Antriebsvolumen 27 betätigt, d.h. mit steigendem Öldruck wird es von der Sperrstellung über die Durchlassstellung mit regelbarem Querschnitt in die Durchlasstellung mit konstantem Querschnitt gedrückt. Gegen diesen Öldruck im Antriebsvolumen 27 arbeitet der Druck im Antriebsvolumen 44 und die Kraft der Feder 42. Der Ausgang 41 ist über eine Leitung 46 mit einem Anschluss 47 verbunden, der eine Verbindung herstellt mit dem Antriebsvolumen 7 des Stellantriebs 1. Zudem ist dieser Anschluss 47 mit einem Eingang 48 des zweiten Steuerventils 21 verbunden.The first control valve 17 is shown in the closed state in FIG. 1, specifically a seat valve 40 prevents the inlet 16 from being connected through to an outlet 41. The input 16 is connected to a drive volume 44 via a line 43. A pressure building up in this drive volume 44 acts in the same direction as the force of a spring 42, that is to say counter to the pressure prevailing in the drive volume 27. As a rule, however, the piston area belonging to the drive volume 44 is smaller than that of the piston belonging to the drive volume 27, so that it is ensured that the control valve 17 can always be actuated solely by the pressure of the safety oil. The first control valve 17 has three schematically illustrated switching positions, of which the uppermost, the blocking position, has already been described, the middle position shows a passage position with a controllable cross section and the bottom one shows a passage position with a constant cross section. The control valve 17 is actuated by oil pressure in the drive volume 27, i.e. as the oil pressure rises, it is pressed from the blocking position through the open position with adjustable cross section to the open position with constant cross section. The pressure in the drive volume 44 and the force of the spring 42 work against this oil pressure in the drive volume 27. The outlet 41 is connected via a line 46 to a connection 47 which establishes a connection with the drive volume 7 of the actuator 1. In addition, this connection is 47 connected to an input 48 of the second control valve 21.

Der Eingang 48 des zweiten Steuerventils 21 ist in der gezeigten Durchlassstellung zu einem Ausgang 49 durchverbunden. Der Ausgang 49 ist über eine Leitung 50 mit der Leitung 31 verbunden. Das zeite Steuerventil 21 weist drei schematisch dargestellte Schaltstellungen auf, von denen die oberste als Durchlassstellung mit konstantem Querschnitt wirkt. Die mittlere Schaltstellung wirkt als Durchlassstellung mit regelbarem Querschnitt und die unterste als Sperrstellung. Das Steuerventil 21 wird durch Öldruck im Antriebsvolumen 20 betätigt, d.h. mit steigendem Öldruck wird es von der Durchlassstellung mit konstantem Querschnitt über die Durchlassstellung mit regelbarem Querschnitt in die Sperrstellung gedrückt. Gegen diesen Öldruck im Antriebsvolumen 20 arbeitet die Kraft einer Feder 51. Die Sperrstellung wird durch ein Sitzventil 52 realisiert. Der Eingang 48 ist zudem über eine Leitung 53 mit einem Antriebsvolumen 54 verbunden. Ein sich in diesem Antriebsvolumen 54 aufbauender Druck wirkt in die gleiche Richtung wie die Kraft der Feder 51, also entgegen dem im Antriebsvolumen 20 herrschenden Druck. In der Regel ist jedoch die zum Antriebsvolumen 54 gehörige Kolbenfläche kleiner als die des zum Antriebsvolumen 20 gehörenden Kolbens, sodass sichergestellt ist, dass das Steuerventil 21 stets allein durch den Druck des Sicherheitsöls betätigt werden kann.
Die beiden Steuervertile 17 und 21 weisen, wie bereits beschrieben, jeweils eine Durchlassstellung mit regelbaren Querschnitt mit jeweils einer bestimmten Regelcharakteristik auf. Diese Regelcharakteristik kann nun in beiden Steuerventilen 17, 21 gleich ausgebildet sein, wobei die zu regelnden Querschnitte unterschiedlich ausgebildet sein können. Es ist jedoch auch möglich, dass diese Regelcharakteristik in jedem der beiden Steuerventile 17, 21 unterschiedlich ausgebildet ist. Durch diese verschiedenen Regelcharakteristiken ist es möglich, die Steuerventile 17, 21 optimal aneinander und an die jeweiligen Betriebsanforderungen anzupassen, so dass der Antrieb in einem vergleichsweise grossen Anwendungsbereich eingesetzt werden kann. Etwa nötige Anpassungen an erweiterte Betriebsanforderungen lassen sich vergleichsweise einfach durchführen, da nur die Geometrie im Bereich des regelbaren Querschnitts geändert werden muss.In the passage position shown, the inlet 48 of the second control valve 21 is connected to an outlet 49. The output 49 is connected to the line 31 via a line 50. The second control valve 21 has three schematically illustrated switching positions, the uppermost of which acts as a passage position with a constant cross section. The middle switching position acts as an open position with an adjustable cross-section and the lowest as a blocking position. The control valve 21 is actuated by oil pressure in the drive volume 20, ie with increasing oil pressure, it is pressed from the open position with a constant cross section through the open position with a controllable cross section into the blocking position. The force of a spring 51 works against this oil pressure in the drive volume 20. The blocking position is realized by a seat valve 52. The input 48 is also connected to a drive volume 54 via a line 53. A pressure building up in this drive volume 54 acts in the same direction as the force of the spring 51, that is to say counter to the pressure prevailing in the drive volume 20. As a rule, however, the piston area belonging to the drive volume 54 is smaller than that of the piston belonging to the drive volume 20, so that it is ensured that the control valve 21 can always be actuated solely by the pressure of the safety oil.
As already described, the two control valves 17 and 21 each have a passage position with an adjustable cross section, each with a specific control characteristic. This control characteristic can now be configured identically in both control valves 17, 21, the cross sections to be controlled being configured differently. However, it is also possible for this control characteristic to be designed differently in each of the two control valves 17, 21. These different control characteristics make it possible to optimally adapt the control valves 17, 21 to one another and to the respective operating requirements, so that the drive can be used in a comparatively large area of application. Any necessary adjustments to extended operating requirements can be made comparatively easily carry out, since only the geometry in the area of the adjustable cross-section needs to be changed.

Das erste Proportional-Druckventil 29 wirkt ähnlich wie eine regelbare Blende, bei welcher einerseits die Blendenöffnung über eine Leitung 55 mit Hilfe des anstehenden Öldrucks vergrössert werden soll, während andererseits gleichzeitig ein Elektromagnet 56, gegen diesen Öldruck arbeitend, die Blendenöffnung verkleinern will. Eine Wirkungslinie 57 deutet an, dass der Elektromagnet 56 durch eine elektronische Regelanordnung 58 gezielt betätigt wird. Entsprechend dem ersten Proportional-Druckventil 29 wirkt auch das zweite Proportional-Regelventil 34, bei welchem der Öldruck über eine Leitung 59 in Öffnungsrichtung und ein Elektromagnet 60 in Schliessrichtung wirkt. Eine Wirkungslinie 61 deutet an, dass der Elektromagnet 60 ebenfalls durch die elektronische Regelanordnung 58 gezielt betätigt wird. Die elektronische Regelanordnung 58 steht zudem, wie durch eine Wirkungslinie 62 angedeutet, in Wirkverbindung mit der Wegmesseinrichtung 11. Eine Wirkungslinie 63 deutet an, dass in die elektronische Regelanordnung 58 auch Befehle und Signale einer übergeordneten Anlagenleittechnik eingegeben und in ihr umgesetzt werden.The first proportional pressure valve 29 acts similarly to an adjustable orifice, in which on the one hand the orifice opening is to be enlarged via a line 55 with the aid of the oil pressure present, while on the other hand an electromagnet 56, working against this oil pressure, wants to reduce the orifice opening. A line of action 57 indicates that the electromagnet 56 is selectively actuated by an electronic control arrangement 58. Corresponding to the first proportional pressure valve 29, the second proportional control valve 34 also acts, in which the oil pressure acts via a line 59 in the opening direction and an electromagnet 60 in the closing direction. A line of action 61 indicates that the electromagnet 60 is also selectively actuated by the electronic control arrangement 58. The electronic control arrangement 58 is also, as indicated by an action line 62, in operative connection with the displacement measuring device 11. An action line 63 indicates that commands and signals of a higher-level system control system are also entered into the electronic control arrangement 58 and implemented therein.

Die beiden Proportional-Druckventile 29 und 34 sind als Sitzventile ausgebildet, sodass eine etwaige Zersetzung oder ein Verharzen des Öls die Funktion dieser Ventile nicht beeinträchtigen kann. Durch die Sitzbauweise werden eine vergleichsweise hohe Sicherheit und Verfügbarkeit dieser Ventile erreicht. Es ist jedoch auch möglich an diesen Stellen der Anordnung Servoventile einzusetzen.The two proportional pressure valves 29 and 34 are designed as seat valves, so that any decomposition or resinification of the oil cannot impair the function of these valves. Due to the seat construction, a comparatively high level of safety and availability of these valves is achieved. However, it is also possible to use servo valves at these points in the arrangement.

Die Ausführung gemäss Fig. 2 entspricht nahezu vollständig der in Fig. 1 dargestellten Ausführung, lediglich die Steuerventile 17 und 21 sind jeweils zusätzlich mit einer Wegmesseinrichtung 65 und 66 versehen. Die von der Wegmesseinrichtung 65 abgegebenen Signale werden, wie durch eine Wirkungslinie 67 angedeutet, in die elektronische Regelanordnung 58 eingespeist und dort weiter umgesetzt. Die von der Wegmesseinrichtung 66 abgegebenen Signale werden, wie durch eine Wirkungslinie 68 angedeutet, in die elektronische Regelanordnung 58 eingespeist und dort weiter verarbeitet.The embodiment according to FIG. 2 corresponds almost completely to the embodiment shown in FIG. 1, only the control valves 17 and 21 are each additionally provided with a displacement measuring device 65 and 66. The signals emitted by the displacement measuring device 65 become, as by an action line 67 indicated, fed into the electronic control arrangement 58 and further implemented there. The signals emitted by the displacement measuring device 66 are, as indicated by an action line 68, fed into the electronic control arrangement 58 and further processed there.

Die Ausführung gemäss Fig. 3 weist gegenüber der Ausführung gemäss Fig. 1 lediglich ein einziges Proportional-Druckventil 29 auf, welches über die Leitung 15 und die Blende 26 mit Öl unter Druck beaufschlagt wird. Das Antriebsvolumen 27 des Steuerventils 17 wird, wie bereits beschrieben, mit diesem Öl unter Druck beaufschlagt. Zudem zweigt jedoch zwischen der Blende 26 und dem Antriebsvolumen 27 eine Leitung 67 von der Leitung 15 ab. Diese Leitung 67 mündet direkt in das Antriebsvolumen 20 des Steuerventils 21 ein. Die Antriebsvolumina 27 und 20 werden demnach parallel und gleichzeitig mit dem von der Leitung 15 eingespeisten Öl unter Druck beaufschlagt. Die diesem Öl unter Druck entgegenwirkenden Federn 42 und 51 der beiden Steuerventile 17 und 21 sind so angebracht, dass deren Vorspannkraft mechanisch verstellt werden kann, durch Pfeile wird diese Verstellbarkeit symbolisiert.The embodiment according to FIG. 3 has only a single proportional pressure valve 29 compared to the embodiment according to FIG. 1, which is pressurized with oil via the line 15 and the orifice 26. As already described, the drive volume 27 of the control valve 17 is pressurized with this oil. In addition, however, a line 67 branches off from line 15 between orifice 26 and drive volume 27. This line 67 opens directly into the drive volume 20 of the control valve 21. The drive volumes 27 and 20 are therefore acted upon in parallel and simultaneously with the oil fed in from the line 15 under pressure. The springs 42 and 51 of the two control valves 17 and 21 counteracting this oil under pressure are mounted in such a way that their pretensioning force can be adjusted mechanically. This adjustability is symbolized by arrows.

Zur Erläuterung der Wirkungsweise sei die Fig. 1 näher betrachtet. Die Fig. 1 zeigt den Antrieb in der Fail-Save-Stellung, in welcher beispielsweise die Leitung 15 ohne Druckbeaufschlagung ist und in welcher das Dampfstellventil 2 geschlossen ist. Es ist jedoch auch möglich, dass sowohl die Leitung 13 als auch die Leitung 15 druckbeaufschlagt sind, und dass das Dampfstellventil 2 allein durch ein elektrisches Absteuern der Proportional-Druckventile 29 und 34 geschlossen wird. In diesem Fall werden die Elektromagnete 56 und 60 so abgesteuert, dass der durch die Leitungen 55 und 59 anstehende Öldruck die Proportional-Druckventile 29 und 34 auf Durchlass stellt, sodass sich in den Antriebsvolumina 20 und 27 kein Öldruck aufbauen kann. Dies hat zur Folge, dass die Steuerventile 17 und 21 nicht betätigt werden, sodass deren in Fig. 1 dargestellte Stellung beibehalten wird und das Dampfstellventil 2 geschlossen bleibt.To explain the mode of operation, FIG. 1 is considered in more detail. Fig. 1 shows the drive in the fail-save position, in which, for example, the line 15 is without pressure and in which the steam control valve 2 is closed. However, it is also possible for both the line 13 and the line 15 to be pressurized, and for the steam control valve 2 to be closed solely by electrically deactivating the proportional pressure valves 29 and 34. In this case, the electromagnets 56 and 60 are controlled such that the oil pressure present through the lines 55 and 59 sets the proportional pressure valves 29 and 34 to passage, so that no oil pressure can build up in the drive volumes 20 and 27. As a result, the control valves 17 and 21 are not actuated, so that their 1 position is maintained and the steam control valve 2 remains closed.

Soll nun das Dampfstellventil 2 geöffnet werden, so werden die Elektromagnete 56 und 60 von der elektronischen Regelanordnung 58 her gezielt erregt, sodass der Öldurchfluss durch die Proportional-Druckventile 29 und 34 verringert wird. Im Bereich der Leitungen 28 und 33 und damit auch in den Antriebsvolumina 27 und 20 der Steuerventile 17 und 21 baut sich infolgedessen ein Öldruck auf. Dieser Öldruck steigt mit zunehmender Verringerung des Öldurchflusses weiter an. Sobald dieser Öldruck hoch genug ist, um die Gegenkräfte in den Steuerventilen 17 und 21 zu überwinden, so bewegen sich diese aus der Fail-Save-Stellung heraus. Das Steuerventil 17 bewegt sich von der Sperrstellung in die Durchlassstellung mit regelbarem Querschnitt, das Steuerventil 21 von der Durchlassstellung mit konstantem Querschnitt in diejenige mit regelbarem Querschnitt. Durch die Leitungen 13 und 46 strömt nun Öl über den Anschluss 47 in das Antriebsvolumen 7 des Stellantriebs 1 und gleichzeitig durch das Steuerventil 21 und die Leitung 31 in den Ablauf. Strömt durch die Leitung 46 mehr Öl nach, als durch das Steuerventil 21 abfliessen kann, so baut sich im Antriebsvolumen 7 ein Druck auf, der den Stellantrieb 1 und damit auch das Dampfstellventil 2 in Öffnungsrichtung bewegt. Die Wegmesseinrichtung 11 liefert wegabhängige Signale in die elektronische Regelanordnung 58, wo sie ausgewertet und mit einem vorgegebenen Sollwert verglichen werden. Dieser Sollwert wird durch eine übergeordnete Anlagenleittechnik vorgegeben. Entsprechend dem Resultat dieses Soll-Ist-Vergleichs wird von der elektronischen Regelanordnung 58 aus die Erregung der Elektromagnete 56 und 60 geändert, wodurch auch die Stellung der regelbaren Steuerventile 17 und 21 entsprechend verändert wird. Sollte eine zu grosse Ölmenge in das Antriebsvolumen 7 fliessen, wird jedoch die Blende 14 wirksam, welche einen weiteren Anstieg der fliessenden Ölmenge verhindert. Die Blende 14 begrenzt die Öffnungszeit des Stellantriebs 1, sodass im Stellantrieb 1 wegen etwa zu schnell bewegter und abzubremsender Massen keine mechanischen Defekte auftreten können. Ferner wirkt sich diese Öffnungszeitbegrenzung positiv aus auf das Betriebsverhalten der Turbine, die so keinen stossartigen Belastungen mit Heissdampf unterworfen wird.If the steam control valve 2 is now to be opened, the electromagnets 56 and 60 are selectively excited by the electronic control arrangement 58, so that the oil flow through the proportional pressure valves 29 and 34 is reduced. As a result, an oil pressure builds up in the area of the lines 28 and 33 and thus also in the drive volumes 27 and 20 of the control valves 17 and 21. This oil pressure increases as the oil flow decreases. As soon as this oil pressure is high enough to overcome the opposing forces in the control valves 17 and 21, they move out of the fail-save position. The control valve 17 moves from the blocking position to the open position with a controllable cross section, the control valve 21 from the open position with a constant cross section to that with a controllable cross section. Oil now flows through the lines 13 and 46 via the connection 47 into the drive volume 7 of the actuator 1 and at the same time through the control valve 21 and the line 31 into the drain. If more oil flows in through line 46 than can flow off through control valve 21, pressure builds up in drive volume 7, which moves actuator 1 and thus also steam control valve 2 in the opening direction. The path measuring device 11 delivers path-dependent signals into the electronic control arrangement 58, where they are evaluated and compared with a predetermined target value. This setpoint is specified by a higher-level system control system. In accordance with the result of this target / actual comparison, the excitation of the electromagnets 56 and 60 is changed by the electronic control arrangement 58, as a result of which the position of the controllable control valves 17 and 21 is also changed accordingly. If an excessive amount of oil flows into the drive volume 7, however, the orifice 14 becomes effective, which prevents a further increase in the amount of oil flowing. The aperture 14 limits the opening time of the actuator 1, so that in the actuator 1 about fast moving and braking masses no mechanical defects can occur. Furthermore, this opening time limitation has a positive effect on the operating behavior of the turbine, which is not subjected to sudden loads with hot steam.

Der Hauptkolben 6 wird durch das in das Antriebsvolumen 7 eingespeiste Öl nach oben gedrückt, gleichzeitig strömt das im Puffervolumen 8 befindliche Öl durch die Leitung 31 in den Ablauf. Die Öffnungsbewegung des Stellantriebs 1 läuft vergleichsweise langsam ab, das Schliessen muss jedoch aus Sicherheitsgründen sehr rasch erfolgen. Bei der Schliessbewegung des Stellantriebs 1 strömt das Öl aus dem Antriebsvolumen 7 durch das Steuerventil 21, die Leitung 50 und den oberen Teil der Leitung 31 direkt in das Puffervolumen 8. Auf diese Weise gelingt es, das Öl auf kürzestem Weg und damit sehr rasch aus dem Antriebsvolumen 7 zu entfernen, wodurch in Schliessrichtung eine vorteilhaft hohe Dynamik des Stellantriebs 1 erreicht wird.The main piston 6 is pressed upward by the oil fed into the drive volume 7, at the same time the oil in the buffer volume 8 flows through the line 31 into the outlet. The opening movement of the actuator 1 is comparatively slow, but the closing must be done very quickly for safety reasons. During the closing movement of the actuator 1, the oil flows from the drive volume 7 through the control valve 21, the line 50 and the upper part of the line 31 directly into the buffer volume 8. In this way, the oil can be discharged in the shortest possible way and thus very quickly to remove the drive volume 7, whereby an advantageously high dynamic of the actuator 1 is achieved in the closing direction.

Die Ausführung gemäss Fig. 2 ermöglicht eine noch feinfühligere und raschere Annäherung an den vorgegebenen Sollwert, da die Signale der Wegmesseinrichtungen 65, 66 zusätzlich in der elektronischen Regelanordnung 58 verarbeitet werden, wodurch eine raschere und genauere Erreichung des Sollwertes der Antriebsstellung möglich wird. Die Wirkungsweise dieser Anordnung ist im übrigen gleich wie bei der Anordnung gemäss Fig. 1.The embodiment according to FIG. 2 enables an even more sensitive and rapid approximation to the predetermined setpoint, since the signals from the path measuring devices 65, 66 are additionally processed in the electronic control arrangement 58, which enables the setpoint of the drive position to be reached more quickly and more precisely. The mode of operation of this arrangement is otherwise the same as for the arrangement according to FIG. 1.

Die Ausführung gemäss Fig. 3 arbeitet ebenfalls ähnlich wie die Ausführung gemäss Fig. 1. Der Druckaufbau in den Antriebsvolumina 27 und 20 wird hier jedoch mit Hilfe nur eines Proportional-Druckventils 29 erreicht, sodass beide Antriebsvolumina 27 und 20 zugleich und identisch mit Druck beaufschlagt werden. Etwaige Einstellungen des Ansprechverhaltens der Regelventile 17 und 21 können hier bei der Inbetriebsetzung der Anlage mit Hilfe der jeweils einstellbaren Vorspannkraft der Federn 42 und 51 vorgenommen werden, sodass auch hier, trotz identischer Druckbeaufschlagung, den jeweiligen Betriebsaufgaben der Steuerventile 17 und 21 entsprechende, unterschiedliche Ansprechzeitpunkte eingestellt werden können. Mit vergleichsweise geringem Aufwand kann diese vereinfachte Ausführung einen vergleichsweise grossen Anforderungsbereich wirtschaftlich vertretbar abdecken.The embodiment according to FIG. 3 also works similarly to the embodiment according to FIG. 1. However, the pressure build-up in the drive volumes 27 and 20 is achieved here with the aid of only one proportional pressure valve 29, so that both drive volumes 27 and 20 are pressurized simultaneously and identically will. Any settings for the response behavior of the control valves 17 and 21 can be made here when the system is started up using the adjustable preload force of the springs 42 and 51 are carried out, so that here, despite identical pressurization, the respective operating tasks of the control valves 17 and 21 can be set to different response times. With a comparatively low outlay, this simplified embodiment can cover a comparatively large range of requirements in an economically justifiable manner.

Als besonders vorteilhaft wirkt sich jedoch aus, dass dieser Antrieb für ein Dampfstellventil 2 für die Betätigung durch hohe Öldrücke geeignet ist, und zwar sind Drücke bis zum Bereich von 200 bar und höher möglich. Diese hohen Drücke beeinflussen die Betriebssicherheit und die Verfügbarkeit des Antriebs nicht negativ, da an allen Dichtungsstellen, wo diese hohen Drücke auftreten, Sitzventile vorgesehen sind, deren Betriebsverhalten durch eine etwaige Ölverharzung nicht beeinträchtigt wird, insbesondere sind dies die Proportional-Druckventile 29 und 34 und die Sitzventile 40 und 52 der Steuerventile 17 und 21. Der durch den hohen Betätigungsdruck erzielte Dynamikgewinn der Anordnung lässt sich demnach vorteilhaft und vollumfänglich ausnützen für eine Verbesserung des Regelverhaltens der Anordnung.However, it is particularly advantageous that this drive for a steam control valve 2 is suitable for actuation by high oil pressures, namely pressures of up to 200 bar and higher are possible. These high pressures do not negatively influence the operational safety and the availability of the drive, since seat valves are provided at all sealing points where these high pressures occur, the operating behavior of which is not impaired by any oil resinification, in particular these are the proportional pressure valves 29 and 34 and the seat valves 40 and 52 of the control valves 17 and 21. The dynamic gain of the arrangement achieved by the high actuation pressure can therefore be used advantageously and in full to improve the control behavior of the arrangement.

Claims (9)

Antrieb für ein Dampfstellventil (2) mit einer Steuerventilanordnung zur Regelung des Betätigungsdrucks eines Stellantriebs (1), wobei die Steuerventilanordnung mindestens zwei regelbare Steuerventile (17, 21) aufweist, und die mindestens zwei Steuerventile (17, 21) über mindestens ein Vorsteuer-Regelventil druckbeaufschlagt sind, dadurch gekennzeichnet, - dass jedes der mindestens zwei Steuerventile (17, 21) eine Durchlassstellung mit konstantem Querschnitt und eine Durchlassstellung mit regelbarem Querschnitt aufweist. Drive for a steam control valve (2) with a control valve arrangement for regulating the actuating pressure of an actuator (1), the control valve arrangement having at least two controllable control valves (17, 21), and the at least two control valves (17, 21) via at least one pilot control valve are pressurized, characterized in that - That each of the at least two control valves (17, 21) has a passage position with a constant cross section and a passage position with a controllable cross section. Antrieb nach Anspruch 1, dadurch gekennzeichnet, - dass die Durchlassstellung mit regelbarem Querschnitt in jedem der mindestens zwei Steuerventile (17, 21) die gleiche Regelcharakteristik aufweist, und - dass diese Regelcharakteristik in den mindestens zwei Steuerventilen (17, 21) gleichzeitig oder zeitlich verschoben wirksam wird. Drive according to claim 1, characterized in - That the passage position with adjustable cross section in each of the at least two control valves (17, 21) has the same control characteristic, and - That this control characteristic in the at least two control valves (17, 21) takes effect simultaneously or at different times. Antrieb nach Anspruch 1, dadurch gekennzeichnet, - dass die Durchlassstellung mit regelbarem Querschnitt in jedem der mindestens zwei Steuerventile (17,21) eine unterschiedliche Regelcharakteristik aufweist. Drive according to claim 1, characterized in - That the passage position with adjustable cross section in each of the at least two control valves (17, 21) has a different control characteristic. Antrieb nach Anspruch 1, dadurch gekennzeichnet, - dass die mindestens zwei Steuerventile (17, 21) über jeweils mindestens ein Vorsteuer-Regelventil druckbeaufschlagt sind. Drive according to claim 1, characterized in - That the at least two control valves (17, 21) are each pressurized via at least one pilot control valve. Antrieb nach einem der Ansprüche 1 oder 4, dadurch gekennzeichnet, - dass das mindestens eine Vorsteuer-Regelventil von einer elektronischen Regelanordnung (58) her gezielt elektrisch betätigt wird in Abhängigkeit von einer gemessenen Stellung des Stellantriebs (1) und einem vorgegebenen Sollwert dieser Stellung. Drive according to one of claims 1 or 4, characterized in that - That the at least one pilot control valve is selectively actuated electrically by an electronic control arrangement (58) as a function of a measured position of the actuator (1) and a predetermined target value of this position. Antrieb nach Anspruch 5, dadurch gekennzeichnet, - dass als das mindestens eine Vorsteuer-Regelventil ein Proportional-Druckventil (29, 34) oder ein Servoventil vorgesehen ist. Drive according to claim 5, characterized in - That a proportional pressure valve (29, 34) or a servo valve is provided as the at least one pilot control valve. Antrieb nach Anspruch 6, dadurch gekennzeichnet, - dass das Proportional-Druckventil (29, 34) als Sitzventil ausgebildet ist. Drive according to claim 6, characterized in - That the proportional pressure valve (29, 34) is designed as a seat valve. Antrieb nach Anspruch 1, dadurch gekennzeichnet, - dass jedes der mindestens zwei Steuerventile (17, 21) mindestens eine Durchlassstellung und eine Sperrstellung aufweist, und - dass eine in der Sperrstellung wirksame Dichtungsstelle als Sitzventil (40, 52) ausgebildet ist. Drive according to claim 1, characterized in - That each of the at least two control valves (17, 21) has at least one open position and a blocking position, and - That a sealing point effective in the blocking position is designed as a seat valve (40, 52). Antrieb nach Anspruch 5, dadurch gekennzeichnet, - dass die mindestens zwei Steuerventile (17, 21) mit jeweils einer Wegmesseinrichtung (65, 66) versehen sind, und - dass von der jeweils einen Wegmesseinrichtung (65, 66) abgegebene Messignale in die elektronische Regelanordnung (58) zur weiteren Verarbeitung eingespeist werden. Drive according to claim 5, characterized in - That the at least two control valves (17, 21) are each provided with a displacement measuring device (65, 66), and - That measurement signals emitted by the respective distance measuring device (65, 66) are fed into the electronic control arrangement (58) for further processing.
EP91104112A 1990-04-09 1991-03-16 Actuation system for a steam regulating valve Revoked EP0451543B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1204/90 1990-04-09
CH1204/90A CH681380A5 (en) 1990-04-09 1990-04-09

Publications (2)

Publication Number Publication Date
EP0451543A1 true EP0451543A1 (en) 1991-10-16
EP0451543B1 EP0451543B1 (en) 1994-07-13

Family

ID=4204939

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91104112A Revoked EP0451543B1 (en) 1990-04-09 1991-03-16 Actuation system for a steam regulating valve

Country Status (8)

Country Link
US (1) US5095804A (en)
EP (1) EP0451543B1 (en)
JP (1) JPH04224303A (en)
AT (1) ATE108512T1 (en)
CH (1) CH681380A5 (en)
DE (1) DE59102144D1 (en)
DK (1) DK0451543T3 (en)
ES (1) ES2058962T3 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0487919A1 (en) * 1990-11-26 1992-06-03 Leybold Aktiengesellschaft Leak detector apparatus
EP0540963A1 (en) * 1991-11-04 1993-05-12 Asea Brown Boveri Ag Supply circuit for split hydraulic system
EP0604805A1 (en) * 1992-12-28 1994-07-06 Asea Brown Boveri Ag Actuating device for hydraulic actuator with pressure proportional control signal
EP0766010A2 (en) * 1995-09-26 1997-04-02 Rothenberger Werkzeuge-Maschinen GmbH Hydraulic operated hand tool
WO2019121416A1 (en) * 2017-12-21 2019-06-27 Moog Gmbh Actuating drive having a hydraulic outflow booster

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9421149D0 (en) * 1994-10-20 1994-12-07 Smiths Industries Plc Hydraulic systems
US5568759A (en) * 1995-06-07 1996-10-29 Caterpillar Inc. Hydraulic circuit having dual electrohydraulic control valves
JP4369292B2 (en) * 2004-05-06 2009-11-18 タイコ フローコントロールジャパン株式会社 Emergency shut-off valve device
CN101871840B (en) * 2010-07-12 2011-07-20 山东电力研究院 Online test method for flow characteristics of turbine high-pressure governing valve
CN103438040A (en) * 2013-08-21 2013-12-11 上海汇益控制系统股份有限公司 Hydraulic control device of high-pressure regulating valve
EP3425213B1 (en) * 2017-07-03 2020-11-25 LEONARDO S.p.A. Safety valve and method for controlling a hydraulic circuit

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2411525A1 (en) * 1973-03-23 1974-10-03 Stal Laval Turbin Ab HYDRAULIC SERVO SYSTEM FOR STEAM TURBINES
US4276810A (en) * 1972-11-08 1981-07-07 Control Concepts, Inc. Programmed valve system used for positioning control
US4401009A (en) * 1972-11-08 1983-08-30 Control Concepts, Inc. Closed center programmed valve system with load sense
EP0127027A1 (en) * 1983-05-30 1984-12-05 BBC Brown Boveri AG Electro-hydraulic actuator for turbine valves

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3620129A (en) * 1970-07-15 1971-11-16 Gen Signal Corp Hydraulic power circuit with emergency lowering provisions
US4165613A (en) * 1978-03-27 1979-08-28 Koehring Company Control apparatus for a plurality of simultaneously actuatable fluid motors
US4275691A (en) * 1979-02-05 1981-06-30 Wolff George D Electromechanical precision governor for internal combustion engines
DE3140266A1 (en) * 1981-10-10 1983-04-28 Mannesmann Rexroth GmbH, 8770 Lohr "DEVICE FOR CONTROLLING A HYDROMOTOR"
DE3201546C2 (en) * 1982-01-20 1986-03-27 Mannesmann Rexroth GmbH, 8770 Lohr Device for controlling a hydraulic motor
JPS6213204U (en) * 1985-07-10 1987-01-27
US4741247A (en) * 1986-09-17 1988-05-03 Rexa Corporation Pneumatic actuator apparatus
DE3804744A1 (en) * 1988-02-16 1989-08-24 Danfoss As CONTROL DEVICE FOR A HYDRAULIC ACTUATOR

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4276810A (en) * 1972-11-08 1981-07-07 Control Concepts, Inc. Programmed valve system used for positioning control
US4401009A (en) * 1972-11-08 1983-08-30 Control Concepts, Inc. Closed center programmed valve system with load sense
DE2411525A1 (en) * 1973-03-23 1974-10-03 Stal Laval Turbin Ab HYDRAULIC SERVO SYSTEM FOR STEAM TURBINES
EP0127027A1 (en) * 1983-05-30 1984-12-05 BBC Brown Boveri AG Electro-hydraulic actuator for turbine valves

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0487919A1 (en) * 1990-11-26 1992-06-03 Leybold Aktiengesellschaft Leak detector apparatus
US5369982A (en) * 1990-11-26 1994-12-06 Leybold Aktiengesellschaft Leak detector
EP0540963A1 (en) * 1991-11-04 1993-05-12 Asea Brown Boveri Ag Supply circuit for split hydraulic system
US5280807A (en) * 1991-11-04 1994-01-25 Asea Brown Boveri Ltd. Supply circuit for a two-tube hydraulic system
EP0604805A1 (en) * 1992-12-28 1994-07-06 Asea Brown Boveri Ag Actuating device for hydraulic actuator with pressure proportional control signal
EP0766010A2 (en) * 1995-09-26 1997-04-02 Rothenberger Werkzeuge-Maschinen GmbH Hydraulic operated hand tool
EP0766010A3 (en) * 1995-09-26 1999-05-06 Rothenberger Werkzeuge-Maschinen GmbH Hydraulic operated hand tool
WO2019121416A1 (en) * 2017-12-21 2019-06-27 Moog Gmbh Actuating drive having a hydraulic outflow booster
CN111566357A (en) * 2017-12-21 2020-08-21 穆格股份有限公司 Actuating drive with hydraulic drainage booster
CN111566357B (en) * 2017-12-21 2022-06-17 穆格股份有限公司 Actuating drive with hydraulic drainage booster

Also Published As

Publication number Publication date
EP0451543B1 (en) 1994-07-13
ES2058962T3 (en) 1994-11-01
DE59102144D1 (en) 1994-08-18
DK0451543T3 (en) 1994-10-31
US5095804A (en) 1992-03-17
JPH04224303A (en) 1992-08-13
ATE108512T1 (en) 1994-07-15
CH681380A5 (en) 1993-03-15

Similar Documents

Publication Publication Date Title
DE1921977C3 (en) Valve device for controlling the pressure medium paths of a double-acting servo motor
DE3305092C2 (en)
EP0451543B1 (en) Actuation system for a steam regulating valve
WO2011154056A1 (en) Valve arrangement
LU88558A1 (en) Pilot operated servo valve
DE19634319A1 (en) Electro-hydraulic control device
DE4036564A1 (en) Hydraulic system for control of press RAM - provides fast approach with high forming load by use of nested cylinders controlled by multiway proportional valve
CH628117A5 (en) Brake-valve device
EP0430089B1 (en) Actuator
EP0041247A2 (en) Pilot-operated device for load-independent flow control
EP0604805B1 (en) Actuating device for hydraulic actuator with pressure proportional control signal
EP0631056B1 (en) Actuator for a control valve
DE3225132A1 (en) Hydraulic safety brake valve
DE3011196C2 (en)
DE3418261C2 (en)
DE2717418A1 (en) DEVICE FOR PRESSURE TESTING AND CONTROL OF A SAFETY VALVE
EP0624732B1 (en) Hydraulic control device
DE3630454C1 (en) Device for controlling hydraulic drives
DE102018116487A1 (en) Electromagnetic adjusting device, in particular for opening and closing a valve device, valve device with such an adjusting device, controllable vibration damper comprising such an adjusting device and motor vehicle with such a vibration damper
DE3224955C2 (en) Proportional valve
DE3321778A1 (en) DEVICE AND METHOD FOR LOCKING A SERVO PISTON IN THE EVENT OF A FAULT
DE102004023553B3 (en) Hydraulic valve arrangement, in particular water hydraulic valve arrangement
DE2737653A1 (en) CONTROL UNIT FOR A HYDRAULIC WORK CIRCUIT
DE2947842C2 (en) Hydraulic safety control with pressure stage control valve
DE2915505A1 (en) FORCE LIMITER FOR ONE ROD

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU NL SE

17P Request for examination filed

Effective date: 19920307

17Q First examination report despatched

Effective date: 19930317

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE DK ES FR GB GR IT LI LU NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19940713

Ref country code: BE

Effective date: 19940713

REF Corresponds to:

Ref document number: 108512

Country of ref document: AT

Date of ref document: 19940715

Kind code of ref document: T

REF Corresponds to:

Ref document number: 59102144

Country of ref document: DE

Date of ref document: 19940818

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19941013

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19940916

ET Fr: translation filed
REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2058962

Country of ref document: ES

Kind code of ref document: T3

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GR

Payment date: 19950228

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19950316

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19950331

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19950331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19950331

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: HELMUT BAELZ GMBH

Effective date: 19950412

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19960215

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19960220

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 19960222

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19960320

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 19960321

Year of fee payment: 6

RDAH Patent revoked

Free format text: ORIGINAL CODE: EPIDOS REVO

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT REVOKED

REG Reference to a national code

Ref country code: GR

Ref legal event code: MF4A

Free format text: 3013320

GBPR Gb: patent revoked under art. 102 of the ep convention designating the uk as contracting state

Free format text: 960705

27W Patent revoked

Effective date: 19960705