EP0419946B1 - Valve motor - Google Patents

Valve motor Download PDF

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Publication number
EP0419946B1
EP0419946B1 EP90117575A EP90117575A EP0419946B1 EP 0419946 B1 EP0419946 B1 EP 0419946B1 EP 90117575 A EP90117575 A EP 90117575A EP 90117575 A EP90117575 A EP 90117575A EP 0419946 B1 EP0419946 B1 EP 0419946B1
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EP
European Patent Office
Prior art keywords
valve
control valve
control
pilot control
actuating drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90117575A
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German (de)
French (fr)
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EP0419946A1 (en
Inventor
Heinz Frey
Kamil Prochazka
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ABB Asea Brown Boveri Ltd
ABB AB
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ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Priority to AT90117575T priority Critical patent/ATE103035T1/en
Publication of EP0419946A1 publication Critical patent/EP0419946A1/en
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Publication of EP0419946B1 publication Critical patent/EP0419946B1/en
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    • 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 invention relates to an actuator for a control valve according to the preamble of patent claim 1.
  • the main piston of this actuator is connected via a linkage to a control orifice which interacts with a pilot piston arrangement and regulates the flow of oil to the main piston.
  • a control orifice which interacts with a pilot piston arrangement and regulates the flow of oil to the main piston.
  • This can only be achieved by a complex device integrated in the linkage, such as scenes or cams with a corresponding mechanism.
  • the stroke of the actuator is usually monitored during operation, which is only possible here using a comparatively complex measuring device.
  • the main piston always runs after the piston of the pilot piston arrangement, so that additional measures generally have to be taken in order to avoid overshooting of the main piston. It also has the disadvantage that the actuator function cannot be directly secured by a safety oil circuit.
  • 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 has a higher dynamic range during operation.
  • the single figure shows a schematic representation of an actuator according to the invention.
  • the figure shows an actuator 1, which actuates a control valve 2, which can open and close a schematically illustrated superheated steam line 2a.
  • the control valve 2 is connected to a main piston 4 via a rod 3.
  • a drive volume 5 charged with oil pressure.
  • a schematically indicated master cylinder 7 includes the spring 6, the master piston 4 and the drive volume 5.
  • On the side of the spring 6, a further rod 8 is connected to the main piston 4. This rod 8 penetrates, just like the rod 3, the master cylinder 7. The construction of these pressure-tight penetrations will not be described here.
  • the rod 8 is guided by a guide 9, it is articulated to a rocker 11 via an articulated intermediate piece 10.
  • the rocker 11 is rotatably mounted in an indicated fixed bearing 12.
  • the other end of the rocker 11 is articulated to a rod 13 which interacts with a control panel 14.
  • the rod 13 is provided in the upper region with a part, not shown, which, like the intermediate piece 10 between the rod 8 and the rocker 11, implements the rotary movement of the rocker 1 in a straight line movement of the rods 13 and 8 facilitated.
  • the assembly consisting of the rod 8, the intermediate piece 10, the rocker 11, the bearing 12 and the rod 13 is referred to as the linkage 15.
  • this linkage 15 which is shown in a greatly simplified manner, non-linear links such as, for example, cam disks or link controls can also be provided.
  • the control orifice 14 has a schematically indicated closure piece 16, which is rigidly connected to a piston 17 of a pilot piston arrangement 18.
  • the pilot piston arrangement 18 has an actuating volume 19 above which the piston 17 is subjected to oil pressure and a spring 20 which is provided below the piston 17 and acts thereon.
  • the position of the piston 17 is controlled by a displacement measuring device 21 rigidly connected to it.
  • path-proportional electrical signals emitted by the path measuring device 21 are fed into an electronic controller 31.
  • the controller 31 is, as indicated by a dashed line of action 32, in operative connection with a proportional directional control valve 33.
  • This operative connection comprises, on the one hand, the electromagnetic actuation of the proportional directional control valve 33, which is controlled by the electronic controller 31 according to certain predetermined criteria, and, on the other hand, the path-proportional electrical signals fed back into the controller 31 of a position measuring device 34, which monitors the position of the proportional directional control valve 33.
  • a defined starting position of the proportional directional valve 33 is achieved with the aid of a spring, not shown.
  • the proportional directional control valve 33 also has an additional stroke feedback, not shown, which, together with an electronic position control, also not shown, achieves a proportional control behavior of this proportional directional control valve 33, namely an oil flow rate is set proportional to an electrical signal acting on it.
  • Oil is fed in under pressure through a line 40, and the necessary oil pressure is generated by a pump (not shown).
  • the flow rate of the oil is regulated by an orifice 41 arranged in the line 40.
  • the aperture 41 can either have an opening with a constant cross section or an opening with a controllable cross section.
  • the oil flows into the drive volume 5 and from there, as indicated schematically by the branching line 42, to the control orifice 14, through this further into a line 43, which leads to a drain device, not shown. From this drain device, the oil continues through the aforementioned pump back into line 40.
  • a line 44 branches off with an orifice 44 a, which leads to an inlet 45 of the proportional directional valve 33.
  • An outlet 46 of the proportional directional control valve 33 is connected by a line 47 to the actuating volume 19 of the pilot piston arrangement 18.
  • a line 48 branches off from this line 47 and opens into line 43.
  • a line 50 leads from a further outlet 49 of the proportional directional valve 33, which also opens into line 43.
  • the proportional directional control valve 33 is advantageously arranged in the immediate vicinity of the pilot piston arrangement 18 or flanged together to form a monolithic assembly, as a result of which the line 47 and thus the line volume to be filled with oil are small.
  • the dynamics of the control system are greatly increased by the elimination of pulse lines. All lines that are pressurized with oil pressure are designed with the smallest possible longitudinal extension in order to reduce line volumes and thereby increase the dynamics of the actuator.
  • a safety valve 60 which is designed as a plate valve and has an actuating volume 61 is used here.
  • the safety valve 60 is usually closed, since the actuating volume 61 is so strongly acted upon by a line 62 with the pressure of the safety oil from a safety oil circuit, not shown, that a spring 63 acting in the opening direction of the safety valve cannot relax.
  • the line 48 is also made as short as possible.
  • the proportional directional control valve 33 is switched in such a way that oil can flow out of the actuating volume 19 of the pilot piston arrangement 18 through the lines 47 and 50 into the line 43 and through this into the drain device.
  • the result of this is that the spring 20 can push the piston 17 and with it the closure piece 16 of the control orifice 14 upward, as a result of which the flow cross-section of the control orifice 14 is enlarged.
  • the orifice 41 limits the flow rate of the oil, but since more oil can now flow out through the control orifice 14, the oil pressure in the drive volume 5 drops and the spring 6 presses the main piston 4 down and the control valve 2 is moved in the closing direction.
  • the electronic controller 31 determines on the basis of the incoming path-proportional signals coming from the displacement measuring device 21 that the desired target position of the control valve 2 has been reached. Any non-linearities in the closing behavior of the control valve 2 are compensated in the controller 31. These non-linearities are entered into the controller 31 when this actuator 1 is started up, and any necessary fine adjustments can also be made via an entry into the controller 31.
  • One and the same type of controller can therefore be used for a wide variety of control valves, since only corresponding programming is necessary to adapt the controller.
  • any closing and opening characteristics of the control valve 2 can be set using the controller 31. In this way, complex mechanical changes to the linkage 15 can be avoided that would otherwise be necessary to change the drive characteristics of the actuator 1.
  • the proportional directional control valve 33 is switched over by a command from the controller 31, specifically in such a way that the circuit diagram shown at the top of this valve applies.
  • the inlet 45 is connected to the outlet 46, so that oil, the quantity of which is controlled by the proportional directional control valve 33, can flow through the lines 44 and 47 into the actuating volume 19 of the pilot piston arrangement 18 and can increase the oil pressure there, since through the Line 48 does not drain any oil.
  • the opening speed of the pilot piston arrangement 18 is limited by the aperture 44a.
  • the pilot piston arrangement 18 closes or reduces the flow cross-section of the control orifice 14, so that, fed by the line 40, the oil pressure in the drive volume 5 rises, as a result of which the main piston 4 is moved upward and at the same time the control valve 2 is moved in the opening direction.
  • the controller 31 recognizes this and controls the proportional directional control valve 33, so that no additional oil gets into the actuating volume 19.
  • control valve 2 The function of the control valve 2 must be checked at regular intervals in order to be sure that it can also carry out its closing movement at any time in the event of a fault.
  • an additional oil pressure line had to be led into the pilot piston arrangement 18 for this purpose, so that it could be actuated against the pressure prevailing in the actuating volume 19.
  • the piston 17 was then moved upward, the control orifice 14 was opened, the pressure from the drive volume 5 was able to escape via the control orifice 14 and the control valve 2 carried out a closing movement that was independent of the rest of the control system.
  • This additional oil pressure line had to be equipped with valves and securely sealed off from the rest of the control system in order to avoid unwanted, dangerous actuations of the pilot piston arrangement 18. This elaborate solution is no longer required, since this control can be initiated directly via the controller 31 by corresponding electrical control of the proportional directional valve 33.
  • the safety valve 60 opens immediately when the pressure of the safety oil in the line 62 drops.
  • the oil from the actuating volume 19 of the pilot piston arrangement 18 flows very quickly through the line 48 and the actuator 1 closes the control valve 2 immediately. This closing takes place even in the event of a power failure, since the springs 63, 20 and 6 ensure that the switch-off position is safely reached even without an additional one Ensure energy. In this way, a safe final state of the actuator 1 is always achieved; unstable operating states cannot occur.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Control Of Turbines (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)
  • Control Of Transmission Device (AREA)

Abstract

This actuating drive (1) has a main piston (4) which can be operated by means of an oil pressure and a pilot control system in effective connection to the main piston (4) by means of a linkage (15). The pilot control system includes a control orifice (14) controlling the oil pressure at the main piston (4) and a pilot control piston arrangement (18) which can be operated hydraulically. The actuating drive (1) is to be designed in such a way that it has improved dynamic characteristics during operation. This is achieved by the fact that the pilot control piston arrangement (18) can be operated by means of an electrohydraulic valve which is triggered by an electronic control unit (31).

Description

TECHNISCHES GEBIETTECHNICAL AREA

Die Erfindung geht aus von einem Stellantrieb für ein Regelventil gemäss dem Oberbegriff des Patentanspruchs 1.The invention relates to an actuator for a control valve according to the preamble of patent claim 1.

STAND DER TECHNIKSTATE OF THE ART

Aus der Patentschrift DE 27 48 611 ist ein derartiger Stellantrieb für die Betätigung eines Regelventils, mit welchem beispielsweise die Dampfzufuhr zu einer Turbine geregelt wird, bekannt. Der Stellantrieb weist einen Hauptkolben auf, der einerseits mit Federkraft und andererseits mit Öldruck beaufschlagt ist. Bei nachlassendem Öldruck schliesst die Federkraft sicher das Regelventil, welches also auf jeden Fall die Dampfzufuhr unterbricht. Hierdurch wird sichergestellt, dass die Turbine keinen unkontrollierbaren Betriebszustand erreichen kann, wenn der Öldruck für das Regelventil ausfallen sollte. Bei dieser Ausführung wird ein Stellsignal als Öldruck durch einen zentralen elektrohydraulischen Wandler, der gleichzeitig mehrere Stellantriebe betätigt, erzeugt. Dies bedingt vergleichsweise lange Impulsrohrleitungen für das das Stellsignal übertragende Öl, sodass dieses zwangsläufig entstandene Leitungsvolumen das dynamische Verhalten des Stellantriebs negativ beeinflusst.From the patent DE 27 48 611, such an actuator for the actuation of a control valve, with which, for example, the steam supply to a turbine is regulated, is known. The actuator has a main piston which is acted upon on the one hand by spring force and on the other hand by oil pressure. When the oil pressure drops, the spring force securely closes the control valve, which therefore definitely cuts off the steam supply. This ensures that the turbine cannot reach an uncontrollable operating state if the oil pressure for the control valve should fail. In this version, a control signal is generated as an oil pressure by a central electrohydraulic converter that actuates several actuators at the same time. This requires comparatively long impulse pipelines for the oil that transmits the control signal, so that this inevitably generated line volume has a negative influence on the dynamic behavior of the actuator.

Der Hauptkolben dieses Stellantriebs ist über ein Gestänge mit einer Regelblende verbunden, welche mit einer Vorsteuerkolbenanordnung zusammenwirkt und den Fluss des Öls zum Hauptkolben regelt. Wird eine spezielle Hubcharakteristik des Stellantriebes gewünscht, so kann diese nur durch eine in das Gestänge integrierte, aufwendige Einrichtung, wie beispielsweise Kulissen oder Kurvenscheiben mit entsprechendem Mechanismus, erreicht werden. Der Hub des Stellantriebes wird im Betrieb in der Regel überwacht, was hier nur mittels einer vergleichsweise aufwendigen Messeinrichtung möglich ist. Der Hauptkolben läuft bei einem Regelvorgang stets dem Kolben der Vorsteuerkolbenanordnung nach, sodass in der Regel zusätzliche Massnahmen getroffen werden müssen, um ein Überschwingen des Hauptkolbens zu vermeiden. Zudem wirkt es sich nachteilig aus, dass die Stellantriebsfunktion hier nicht durch einen Sicherheitsölkreis direkt gesichert werden kann.The main piston of this actuator is connected via a linkage to a control orifice which interacts with a pilot piston arrangement and regulates the flow of oil to the main piston. Will be a special one Stroke characteristics of the actuator desired, this can only be achieved by a complex device integrated in the linkage, such as scenes or cams with a corresponding mechanism. The stroke of the actuator is usually monitored during operation, which is only possible here using a comparatively complex measuring device. During a control process, the main piston always runs after the piston of the pilot piston arrangement, so that additional measures generally have to be taken in order to avoid overshooting of the main piston. It also has the disadvantage that the actuator function cannot be directly secured by a safety oil circuit.

Aus der Offenlegungsschrift DE 33 09 441 ist ein elektrohydraulischer Kompaktantrieb bekannt, der einen mittels eines Wegsensors überwachten Hauptkolben aufweist. Bei diesem Kompaktantrieb ist keine Vorsteuerkolbenanordnung vorgesehen.From the published patent application DE 33 09 441 an electrohydraulic compact drive is known which has a main piston monitored by means of a displacement sensor. No pilot piston arrangement is provided for this compact drive.

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 Stellantrieb für ein Regelventil zu schaffen, der im Betrieb eine höhere Dynamik aufweist.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 has a higher dynamic range during operation.

Die durch die Erfindung erreichten Vorteile sind im wesentlichen darin zu sehen, dass allfällige Änderungen der Regelcharakteristik rasch und ohne Änderungen an mechanischen Teilen implementiert werden können. Ferner sind keine Impulsrohrleitungen mehr nötig, sodass einerseits die Dynamik verschlechternde Leitungsvolumina im hydraulischen System auf ein Minimum beschränkt werden und andererseits der Aufbau dieses Systems stark vereinfacht wird. Der Hub des Stellantriebs kann problemlos separat überwacht werden, sodass besonders bei einer Inbetriebsetzungsphase vorteilhaft verkürzte Arbeitszeiten erreicht werden können. Die Sicherheit des Stellantriebs wird erhöht, da sich diese Ausführung über einen Sicherheitsölkreis betätigen lässt.The advantages achieved by the invention are essentially to be seen in the fact that any changes in the control characteristic can be implemented quickly and without changes to mechanical parts. Furthermore, impulse pipelines are no longer necessary, so that on the one hand the dynamics deteriorating line volumes in the hydraulic system are kept to a minimum and on the other hand the structure of this system is greatly simplified. The stroke of the actuator can easily be monitored separately, so that shorter working times can be advantageously achieved, particularly during a commissioning phase. The safety of the actuator is increased because this version can be operated via a safety oil circuit.

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 möglichen 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 possible embodiment.

KURZE BESCHREIBUNG DER ZEICHNUNGBRIEF DESCRIPTION OF THE DRAWING

Die einzige Figur zeigt eine schematische Darstellung eines erfindungsgemässen Stellantriebs.The single figure shows a schematic representation of an actuator according to the invention.

WEGE ZUR AUSFÜHRUNG DER ERFINDUNGWAYS OF CARRYING OUT THE INVENTION

Die Figur zeigt einen Stellantrieb 1, der ein Regelventil 2 betätigt, welches eine schematisch dargestellte Heissdampfleitung 2a öffnen und schliessen kann. Das Regelventil 2 ist über eine Stange 3 mit einem Hauptkolben 4 verbunden. Unterhalb des Hauptkolbens 4 ist hier ein mit Öldruck beaufschlagtes Antriebsvolumen 5 angeordnet. Oberhalb des Hauptkolbens 4 ist eine, dem Öldruck entgegenwirkende Feder 6 vorgesehen. Ein schematisch angedeuteter Hauptzylinder 7 schliesst die Feder 6, den Hauptkolben 4 und das Antriebsvolumen 5 ein. Auf der Seite der Feder 6 ist eine weitere Stange 8 mit dem Hauptkolben 4 verbunden. Diese Stange 8 durchdringt, ebenso wie die Stange 3, den Hauptzylinder 7. Die konstruktive Ausführung dieser druckdichten Durchdringungen soll hier nicht beschrieben werden. Die Stange 8 wird durch eine Führung 9 geführt, sie ist über ein angelenktes Zwischenstück 10 mit einer Schwinge 11 gelenkig verbunden. Die Schwinge 11 ist drehbar in einer angedeuteten festen Lagerstelle 12 gelagert. Das andere Ende der Schwinge 11 ist gelenkig mit einer Stange 13 verbunden, die mit einer Regelblende 14 zusammenwirkt. Die Stange 13 ist im oberen Bereich mit einem nicht dargestellten Teil versehen, welches ähnlich wie das Zwischenstück 10 zwischen der Stange 8 und der Schwinge 11, die Umsetzung der Drehbewegung der Schwinge 1 in eine geradlinige Bewegung der Stangen 13 bzw. 8 erleichtert. Die aus der Stange 8, dem Zwischenstück 10, der Schwinge 11, der Lagerstelle 12 und der Stange 13 bestehende Baugruppe wird als Gestänge 15 bezeichnet. In diesem stark vereinfacht dargestellten Gestänge 15 können auch nichtlineare Glieder wie beispielsweise Kurvenscheiben oder Kulissensteuerungen vorgesehen werden.The figure shows an actuator 1, which actuates a control valve 2, which can open and close a schematically illustrated superheated steam line 2a. The control valve 2 is connected to a main piston 4 via a rod 3. Below the main piston 4 there is arranged a drive volume 5 charged with oil pressure. A spring 6, which counteracts the oil pressure, is provided above the main piston 4. A schematically indicated master cylinder 7 includes the spring 6, the master piston 4 and the drive volume 5. On the side of the spring 6, a further rod 8 is connected to the main piston 4. This rod 8 penetrates, just like the rod 3, the master cylinder 7. The construction of these pressure-tight penetrations will not be described here. The rod 8 is guided by a guide 9, it is articulated to a rocker 11 via an articulated intermediate piece 10. The rocker 11 is rotatably mounted in an indicated fixed bearing 12. The other end of the rocker 11 is articulated to a rod 13 which interacts with a control panel 14. The rod 13 is provided in the upper region with a part, not shown, which, like the intermediate piece 10 between the rod 8 and the rocker 11, implements the rotary movement of the rocker 1 in a straight line movement of the rods 13 and 8 facilitated. The assembly consisting of the rod 8, the intermediate piece 10, the rocker 11, the bearing 12 and the rod 13 is referred to as the linkage 15. In this linkage 15, which is shown in a greatly simplified manner, non-linear links such as, for example, cam disks or link controls can also be provided.

Die Regelblende 14 weist ein schematisch angedeutetes Verschlussstück 16 auf, welches starr mit einem Kolben 17 einer Vorsteuerkolbenanordnung 18 verbunden ist. Die Vorsteuerkolbenanordnung 18 weist ein mit Öldruck beaufschlagtes Betätigungsvolumen 19 oberhalb des Kolbens 17 und eine unterhalb des Kolbens 17 vorgesehene und auf diesen einwirkende Feder 20 auf. Die Stellung des Kolbens 17 wird über eine starr mit diesem verbundene Wegmesseinrichtung 21 kontrolliert. Wie eine gestrichelt ausgeführte Wirkungslinie 30 andeutet, werden von der Wegmesseinrichtung 21 abgegebene, wegproportionale elektrische Signale in einen elektronischen Regler 31 eingespeist. Der Regler 31 steht zudem, wie durch eine gestrichelte Wirkungslinie 32 angedeutet, mit einem Proportional-Wegeventil 33 in Wirkverbindung. Diese Wirkverbindung umfasst einerseits die vom elektronischen Regler 31 nach bestimmten vorgegebenen Kriterien gesteuerte elektromagnetische Betätigung des Proportional-Wegeventils 33 und andererseits die in den Regler 31 zurückgespeisten, wegproportionalen elektrischen Signale einer Wegmesseinrichtung 34, welche die Stellung des Proportional-Wegeventils 33 überwacht. Eine definierte Ausgangsstellung des Proportional-Wegeventils 33 wird mit Hilfe einer nicht dargestellten Feder erreicht. Das Proportional-Wegeventil 33 weist zudem eine zusätzliche, nicht dargestellte Hubrückführung auf, die zusammen mit einer ebenfalls nicht dargestellten elektronischen Positionsregelung ein proportionales Steuerverhalten dieses Proportional-Wegeventils 33 errreicht, und zwar wird dabei eine Öldurchflussmenge proportional zu einem einwirkenden elektrischen Signal eingestellt.The control orifice 14 has a schematically indicated closure piece 16, which is rigidly connected to a piston 17 of a pilot piston arrangement 18. The pilot piston arrangement 18 has an actuating volume 19 above which the piston 17 is subjected to oil pressure and a spring 20 which is provided below the piston 17 and acts thereon. The position of the piston 17 is controlled by a displacement measuring device 21 rigidly connected to it. As indicated by a dashed line of action 30, path-proportional electrical signals emitted by the path measuring device 21 are fed into an electronic controller 31. The controller 31 is, as indicated by a dashed line of action 32, in operative connection with a proportional directional control valve 33. This operative connection comprises, on the one hand, the electromagnetic actuation of the proportional directional control valve 33, which is controlled by the electronic controller 31 according to certain predetermined criteria, and, on the other hand, the path-proportional electrical signals fed back into the controller 31 of a position measuring device 34, which monitors the position of the proportional directional control valve 33. A defined starting position of the proportional directional valve 33 is achieved with the aid of a spring, not shown. The proportional directional control valve 33 also has an additional stroke feedback, not shown, which, together with an electronic position control, also not shown, achieves a proportional control behavior of this proportional directional control valve 33, namely an oil flow rate is set proportional to an electrical signal acting on it.

Durch eine Leitung 40 wird Öl unter Druck eingespeist, der nötige Öldruck wird durch eine nicht dargestellte Pumpe erzeugt. Die Durchflussmenge des Öls wird durch eine im Verlauf der Leitung 40 angeordnete Blende 41 geregelt. Die Blende 41 kann entweder eine Öffnung mit konstantem Querschnitt oder eine Öffnung mit regelbarem Querschnitt aufweisen. Das Öl strömt in das Antriebsvolumen 5 und von dort weiter, wie durch die abzweigende Leitung 42 schematisch angedeutet, zur Regelblende 14, durch diese hindurch weiter in eine Leitung 43, die zu einer nicht dargestellten Ablaufvorrichtung führt. Von dieser Ablaufvorrichtung gelangt das Öl weiter durch die erwähnte Pumpe zurück in die Leitung 40. Von der Leitung 40 zweigt eine Leitung 44 mit einer Blende 44a ab, welche zu einem Eingang 45 des Proportional-Wegeventils 33 führt. Ein Ausgang 46 des Proportional-Wegeventils 33 ist durch eine Leitung 47 mit dem Betätigungsvolumen 19 der Vorsteuerkolbenanordnung 18 verbunden. Von dieser Leitung 47 zweigt eine Leitung 48 ab, welche in die Leitung 43 einmündet. Von einem weiteren Ausgang 49 des Proportional-Wegeventils 33 führt eine Leitung 50 weg, welche ebenfalls in die Leitung 43 einmündet.Oil is fed in under pressure through a line 40, and the necessary oil pressure is generated by a pump (not shown). The flow rate of the oil is regulated by an orifice 41 arranged in the line 40. The aperture 41 can either have an opening with a constant cross section or an opening with a controllable cross section. The oil flows into the drive volume 5 and from there, as indicated schematically by the branching line 42, to the control orifice 14, through this further into a line 43, which leads to a drain device, not shown. From this drain device, the oil continues through the aforementioned pump back into line 40. From line 40, a line 44 branches off with an orifice 44 a, which leads to an inlet 45 of the proportional directional valve 33. An outlet 46 of the proportional directional control valve 33 is connected by a line 47 to the actuating volume 19 of the pilot piston arrangement 18. A line 48 branches off from this line 47 and opens into line 43. A line 50 leads from a further outlet 49 of the proportional directional valve 33, which also opens into line 43.

Das Proportional-Wegeventil 33 wird vorteilhaft in unmittelbarer Nähe der Vorsteuerkolbenanordnung 18 angeordnet oder mit dieser zu einer monolithischen Baugruppe zusammengeflanscht, wodurch die Leitung 47 und damit das mit Öl zu füllende Leitungsvolumen klein ausfällt. Die Dynamik der Regelung wird durch den Wegfall von Impulsleitungen stark erhöht. Sämtliche Leitungen, die mit Öldruck beaufschlagt sind, werden mit möglichst kleiner Längserstreckung ausgeführt, um Leitungsvolumina zu verkleinern und dadurch die Dynamik des Stellantriebes zu erhöhen.The proportional directional control valve 33 is advantageously arranged in the immediate vicinity of the pilot piston arrangement 18 or flanged together to form a monolithic assembly, as a result of which the line 47 and thus the line volume to be filled with oil are small. The dynamics of the control system are greatly increased by the elimination of pulse lines. All lines that are pressurized with oil pressure are designed with the smallest possible longitudinal extension in order to reduce line volumes and thereby increase the dynamics of the actuator.

In der Leitung 48 ist hier ein als Plattenventil ausgebildetes Sicherheitsventil 60 eingesetzt, welches ein Betätigungsvolumen 61 aufweist. Das Sicherheitsventil 60 ist in der Regel geschlossen, da das Betätigungsvolumen 61 von einem nicht dargestellten Sicherheitsölkreis her durch eine Leitung 62 so stark mit dem Druck des Sicherheitsöls beaufschlagt wird, dass eine in Öffnungsrichtung des Sicherheitsventils wirkende Feder 63 sich nicht entspannen kann. Die Leitung 48 wird ebenfalls möglichst kurz ausgebildet.In the line 48, a safety valve 60 which is designed as a plate valve and has an actuating volume 61 is used here. The safety valve 60 is usually closed, since the actuating volume 61 is so strongly acted upon by a line 62 with the pressure of the safety oil from a safety oil circuit, not shown, that a spring 63 acting in the opening direction of the safety valve cannot relax. The line 48 is also made as short as possible.

Zur Erläuterung der Wirkungsweise des Stellantriebes 1 sei die Figur näher betrachtet. Das Proportional-Wegeventil 33 ist so geschaltet, dass vom Betätigungsvolumen 19 der Vorsteuerkolbenanordnung 18 Öl durch die Leitungen 47 und 50 in die Leitung 43 und durch diese in die Ablaufvorrichtung abfliessen kann. Dies hat zur Folge, dass die Feder 20 den Kolben 17 und mit ihm das Verschlussstück 16 der Regelblende 14 nach oben drücken kann, wodurch der Durchströmquerschnitt der Regelblende 14 vergrössert wird. Die Blende 41 begrenzt die Durchflussmenge des Öls, da jedoch jetzt durch die Regelblende 14 mehr Öl abströmen kann, sinkt der Öldruck im Antriebsvolumen 5 ab und die Feder 6 drückt den Hauptkolben 4 nach unten und das Regelventil 2 wird in Schliessrichtung bewegt. Dieser Vorgang setzt sich solange fort, bis der elektronische Regler 31 aufgrund der eingehenden, von der Wegmesseinrichtung 21 herrührenden wegproportionalen Signale feststellt, dass die gewünschte Sollposition des Regelventils 2 erreicht ist. Dabei werden im Regler 31 etwaige Nichtlinearitäten im Schliessverhalten des Regelventils 2 ausgeglichen. Diese Nichtlinearitäten werden bei der Inbetriebsetzung dieses Stellantriebes 1 in den Regler 31 eingegeben, etwa nötige Feineinstellungen können ebenfalls über eine Eingabe in den Regler 31 durchgeführt werden. Ein und derselbe Typ Regler kann demnach für die verschiedensten Regelventile eingesetzt werden, da lediglich entsprechendes Programmieren nötig ist, um den Regler anzupassen. Zudem können mit Hilfe des Reglers 31 beliebige Schliess- und Öffnungscharakteristiken des Regelventils 2 eingestellt werden. Auf diese Art können aufwendige mechanische Abänderungen des Gestänges 15 vermieden werden, die sonst für eine Veränderung der Antriebscharakteristik des Stellantriebs 1 nötig wären.To explain the mode of operation of the actuator 1, the figure is considered in more detail. The proportional directional control valve 33 is switched in such a way that oil can flow out of the actuating volume 19 of the pilot piston arrangement 18 through the lines 47 and 50 into the line 43 and through this into the drain device. The result of this is that the spring 20 can push the piston 17 and with it the closure piece 16 of the control orifice 14 upward, as a result of which the flow cross-section of the control orifice 14 is enlarged. The orifice 41 limits the flow rate of the oil, but since more oil can now flow out through the control orifice 14, the oil pressure in the drive volume 5 drops and the spring 6 presses the main piston 4 down and the control valve 2 is moved in the closing direction. This process continues until the electronic controller 31 determines on the basis of the incoming path-proportional signals coming from the displacement measuring device 21 that the desired target position of the control valve 2 has been reached. Any non-linearities in the closing behavior of the control valve 2 are compensated in the controller 31. These non-linearities are entered into the controller 31 when this actuator 1 is started up, and any necessary fine adjustments can also be made via an entry into the controller 31. One and the same type of controller can therefore be used for a wide variety of control valves, since only corresponding programming is necessary to adapt the controller. In addition, any closing and opening characteristics of the control valve 2 can be set using the controller 31. In this way, complex mechanical changes to the linkage 15 can be avoided that would otherwise be necessary to change the drive characteristics of the actuator 1.

Soll nun das Regelventil 2 wieder geöffnet werden, sodass mehr Dampf durch die Heissdampfleitung 2a in eine Turbine gelangen kann, so wird das Proportional-Wegeventil 33 durch einen Befehl vom Regler 31 her umgeschaltet, und zwar so, dass das zuoberst in diesem Ventil dargestellte Schaltschema gilt. In diesem Fall ist der Eingang 45 durchverbunden zum Ausgang 46, sodass durch die Leitungen 44 und 47 Öl, dessen Menge durch das Proportional-Wegeventil 33 gesteuert wird, in das Betätigungsvolumen 19 der Vorsteuerkolbenanordnung 18 fliessen und dort den Öldruck erhöhen kann, da durch die Leitung 48 kein Öl abfliesst. Durch die Blende 44a wird die Öffnungsgeschwindigkeit der Vorsteuerkolbenanordnung 18 begrenzt. Die Vorsteuerkolbenanordnung 18 schliesst bzw. reduziert den Durchströmquerschnitt der Regelblende 14, sodass, durch die Leitung 40 gespeist, der Öldruck im Antriebsvolumen 5 ansteigt, wodurch der Hauptkolben 4 nach oben und gleichzeitig das Regelventil 2 in Öffnungsrichtung bewegt wird. Sobald der vorgegebene Sollwert erreicht wird, erkennt der Regler 31 dies und steuert das Proportional-Wegeventil 33 ab, sodass kein zusätzliches Öl in das Betätigungsvolumen 19 gelangt.If the control valve 2 is now to be opened again so that more steam can get into a turbine through the hot steam line 2a, the proportional directional control valve 33 is switched over by a command from the controller 31, specifically in such a way that the circuit diagram shown at the top of this valve applies. In this case, the inlet 45 is connected to the outlet 46, so that oil, the quantity of which is controlled by the proportional directional control valve 33, can flow through the lines 44 and 47 into the actuating volume 19 of the pilot piston arrangement 18 and can increase the oil pressure there, since through the Line 48 does not drain any oil. The opening speed of the pilot piston arrangement 18 is limited by the aperture 44a. The pilot piston arrangement 18 closes or reduces the flow cross-section of the control orifice 14, so that, fed by the line 40, the oil pressure in the drive volume 5 rises, as a result of which the main piston 4 is moved upward and at the same time the control valve 2 is moved in the opening direction. As soon as the predetermined target value is reached, the controller 31 recognizes this and controls the proportional directional control valve 33, so that no additional oil gets into the actuating volume 19.

Die Funktion des Regelventils 2 muss in periodischen Abständen kontrolliert werden, um sicher zu sein, dass es im Falle einer Störung auch jederzeit seine Schliessbewegung ausführen kann. Bei herkömmlichen Stellantrieben musste für diesen Zweck eine zusätzliche Öldruckleitung in die Vorsteuerkolbenanordnung 18 geführt werden, sodass diese gegen den im Betätigungsvolumen 19 herrschenden Druck betätigt werden konnte. In diesem Fall wurde dann der Kolben 17 nach oben bewegt, die Regelblende 14 wurde geöffnet, der Druck aus dem Antriebsvolumen 5 konnte über die Regelblende 14 entweichen und das Regelventil 2 führte eine vom übrigen Steuersystem unabhängige Schliessbewegung durch. Diese zusätzliche Öldruckleitung musste mit Ventilen bestückt und gegen das übrige Steuersystem sicher abgeschottet sein, um ungewollte, gefährliche Betätigungen der Vorsteuerkolbenanordnung 18 zu vermeiden. Liese aufwendige Lösung braucht es nun nicht mehr, da diese Kontrolle über den Regler 31 direkt initiiert werden kann durch entsprechende elektrische Ansteuerung des Proportional-Wegeventils 33.The function of the control valve 2 must be checked at regular intervals in order to be sure that it can also carry out its closing movement at any time in the event of a fault. In conventional actuators, an additional oil pressure line had to be led into the pilot piston arrangement 18 for this purpose, so that it could be actuated against the pressure prevailing in the actuating volume 19. In this case, the piston 17 was then moved upward, the control orifice 14 was opened, the pressure from the drive volume 5 was able to escape via the control orifice 14 and the control valve 2 carried out a closing movement that was independent of the rest of the control system. This additional oil pressure line had to be equipped with valves and securely sealed off from the rest of the control system in order to avoid unwanted, dangerous actuations of the pilot piston arrangement 18. This elaborate solution is no longer required, since this control can be initiated directly via the controller 31 by corresponding electrical control of the proportional directional valve 33.

Die Sicherheitsanforderungen an technische Anlagen insbesondere auch an thermische Kraftwerke steigen stetig an. Eine vergleichsweise hohe Sicherheit wird erreicht, wenn ein separater Sicherheitsölkreis erlaubt sämtliche sicherheitsrelevanten Ventile annähernd gleichzeitig zu betätigen. Das Sicherheitsventil 60 öffnet sich sofort, wenn der Druck des Sicherheitsöls in der Leitung 62 abfällt. Das Öl aus dem Betätigungsvolumen 19 der Vorsteuerkolbenanordnung 18 strömt sehr rasch durch die Leitung 48 ab und der Stellantrieb 1 schliesst umgehend das Regelventil 2. Dieses Schliessen erfolgt sogar bei Energieausfall, da die Federn 63, 20 und 6 das sichere Erreichen der Ausschaltstellung auch ohne zusätzliche Energie sicherstellen. Auf diese Art wird immer ein sicherer Endzustand des Stellantriebes 1 erreicht, instabile Betriebszustände können nicht auftreten.The safety requirements for technical systems, especially thermal power plants, are constantly increasing. A comparatively high level of safety is achieved if a separate safety oil circuit allows all safety-relevant valves to be operated almost simultaneously. The safety valve 60 opens immediately when the pressure of the safety oil in the line 62 drops. The oil from the actuating volume 19 of the pilot piston arrangement 18 flows very quickly through the line 48 and the actuator 1 closes the control valve 2 immediately. This closing takes place even in the event of a power failure, since the springs 63, 20 and 6 ensure that the switch-off position is safely reached even without an additional one Ensure energy. In this way, a safe final state of the actuator 1 is always achieved; unstable operating states cannot occur.

Claims (5)

  1. Actuating drive (1) for a control valve (2) having a main piston (4) which can be operated by an oil pressure and having a pilot control system in effective connection with the main piston (4) by means of a linkage (15), which pilot control system has at least one control orifice (14) controlling the oil pressure at the main piston (4) and at least one pilot control piston arrangement (18) which can be hydraulically operated, in which arrangement the at least one pilot control piston arrangement (18) is designed in such a way that it can be operated by means of at least one electrohydraulic valve,
    characterized in that
    - a displacement measurement device (21, 34) emitting an electrical signal is provided on each of the at least one pilot control piston arrangement (18) and the at least one electrohydraulic valve,
    characterized in that
    - these electrical signals are fed into an electronic control unit (31) and are there compared with a required value, and
    - the electronic control unit (31) acts, in the case of deviations from the required value, in a corrective manner on the electrohydraulic valve.
  2. Actuating drive according to Claim 1, characterized in that
    - the at least one electrohydraulic valve is designed as a proportional directional control valve (33).
  3. Actuating drive according to Claim 1, characterized in that
    - the proportional directional control valve (33) is connected to the pilot control piston arrangement to form a monolithic unit.
  4. Actuating drive according to Claim 1, characterized in that
    - compensation is provided for non-linearities of the control valve (2) by non-linear elements in the linkage (15) or by the input of the valve10 characteristics into the electronic control unit (31) or by a combination of both measures.
  5. Actuating drive according to at least one of the preceding claims, characterized in that
    - the closing of the control valve (2) is ensured in the case of faults by means of a safety valve (60).
EP90117575A 1989-09-28 1990-09-12 Valve motor Expired - Lifetime EP0419946B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90117575T ATE103035T1 (en) 1989-09-28 1990-09-12 ACTUATOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3518/89 1989-09-28
CH3518/89A CH678968A5 (en) 1989-09-28 1989-09-28

Publications (2)

Publication Number Publication Date
EP0419946A1 EP0419946A1 (en) 1991-04-03
EP0419946B1 true EP0419946B1 (en) 1994-03-16

Family

ID=4257735

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Application Number Title Priority Date Filing Date
EP90117575A Expired - Lifetime EP0419946B1 (en) 1989-09-28 1990-09-12 Valve motor

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US (1) US5193779A (en)
EP (1) EP0419946B1 (en)
JP (1) JP2974749B2 (en)
AT (1) ATE103035T1 (en)
CH (1) CH678968A5 (en)
DE (1) DE59005002D1 (en)
ES (1) ES2053042T3 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007120679A (en) * 2005-10-28 2007-05-17 Sun Wave Ind Co Ltd Plate material joint structure
US8290631B2 (en) * 2009-03-12 2012-10-16 Emerson Process Management Power & Water Solutions, Inc. Methods and apparatus to arbitrate valve position sensor redundancy
CN106801629B (en) * 2017-03-07 2019-04-12 北京博力威格智能传控设备有限公司 A kind of steam turbine quick-closing valve oil motor device
US20220145774A1 (en) * 2019-03-27 2022-05-12 Salvatore Shifrin Self contained hydraulic lock apparatus

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DE474923C (en) * 1929-04-13 J A Maffei A G Control device on steam turbines
BE464678A (en) * 1945-05-24
DE1601759B2 (en) * 1967-07-19 1972-02-24 Siemens AG, 1000 Berlin u 8000 München HYDRAULICALLY ACTUATED ACTUATOR WITH POWER PISTON, PREFERREDLY FOR OPERATING VALVES FOR LARGE FLOW RATES
SE372055B (en) * 1973-03-23 1974-12-09 Stal Laval Turbin Ab
JPS6014201B2 (en) * 1975-12-01 1985-04-12 黒田精工株式会社 Pneumatic digital cylinder device
CH624187A5 (en) * 1977-09-29 1981-07-15 Bbc Brown Boveri & Cie
US4335867A (en) * 1977-10-06 1982-06-22 Bihlmaier John A Pneumatic-hydraulic actuator system
DE2835771A1 (en) * 1978-08-16 1980-02-28 Schwelm & Towler Hydraulics ARRANGEMENT FOR CONTROLLING A CARTRIDGE ELEMENT
US4215844A (en) * 1978-08-28 1980-08-05 The Babcock & Wilcox Company Valve actuator system
JPS58174701A (en) * 1982-04-07 1983-10-13 Diesel Kiki Co Ltd Hydraulic actuator device
DE3309441A1 (en) * 1983-03-16 1984-09-27 Kraftwerk Union AG, 4330 Mülheim Turbine regulating and control system
EP0127027B1 (en) * 1983-05-30 1988-03-09 BBC Brown Boveri AG Electro-hydraulic actuator for turbine valves
CH666132A5 (en) * 1984-07-20 1988-06-30 Bbc Brown Boveri & Cie DEVICE FOR MONITORING PHYSICAL QUANTITIES IN PLANTS.
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Also Published As

Publication number Publication date
ATE103035T1 (en) 1994-04-15
ES2053042T3 (en) 1994-07-16
DE59005002D1 (en) 1994-04-21
CH678968A5 (en) 1991-11-29
JP2974749B2 (en) 1999-11-10
JPH03121203A (en) 1991-05-23
EP0419946A1 (en) 1991-04-03
US5193779A (en) 1993-03-16

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