EP0127027A1 - Electro-hydraulic actuator for turbine valves - Google Patents

Electro-hydraulic actuator for turbine valves Download PDF

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Publication number
EP0127027A1
EP0127027A1 EP84105238A EP84105238A EP0127027A1 EP 0127027 A1 EP0127027 A1 EP 0127027A1 EP 84105238 A EP84105238 A EP 84105238A EP 84105238 A EP84105238 A EP 84105238A EP 0127027 A1 EP0127027 A1 EP 0127027A1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
quick
hydraulic supply
control valve
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Application number
EP84105238A
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German (de)
French (fr)
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EP0127027B1 (en
Inventor
Jaroslav Masek
Franz Suter
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BBC Brown Boveri AG Switzerland
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BBC Brown Boveri AG Switzerland
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and pump
    • 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
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures
    • Y10T137/87981—Common actuator

Definitions

  • the invention relates to an electro-hydraulic actuator for turbine valves according to the preamble of the claim.
  • the actuators of the individual turbine valves are always supplied with hydraulic energy via a central hydraulic supply system, which comprises a central hydraulic fluid reservoir and usually several fluid pumps working against hydraulic pressure accumulators. Accordingly, at least two pipes are required for connecting an actuator to the central hydraulic supply system, one pipe taking care of supplying the actuator with pressurized hydraulic fluid, while the other pipeline feeds the hydraulic fluid that flows when the hydraulic components are relieved into the central hydraulic fluid reservoir leads back.
  • a central hydraulic supply system which comprises a central hydraulic fluid reservoir and usually several fluid pumps working against hydraulic pressure accumulators.
  • at least two pipes are required for connecting an actuator to the central hydraulic supply system, one pipe taking care of supplying the actuator with pressurized hydraulic fluid, while the other pipeline feeds the hydraulic fluid that flows when the hydraulic components are relieved into the central hydraulic fluid reservoir leads back.
  • the object of the invention is to eliminate the aforementioned disadvantages and an electro-hydraulic actuator for turbine valves, which on the one hand meets the high requirements with regard to actuating force and actuating speed and on the other hand avoids the problems associated with the transmission of hydraulic energy.
  • the electrohydraulic actuator for turbine valves proposed according to the invention to achieve the stated object is characterized in that at least one control valve and at least one quick-closing valve are assigned to each turbine inlet valve, the drives of the same design and integrated into a compact drive unit arranged on the valve housing, these drives being paired with connected directly to a hydraulic supply and are controlled by a vblumetrically controlled oil delivery unit integrated with the hydraulic supply.
  • Another advantage of the invention can be seen in the fact that a hydraulic supply operates one control valve and one quick-closing valve. Because the hydraulic supply is no longer conditioned in terms of space, it can be made more robust, simpler and cheaper.
  • the hydraulic supply includes a volumetrically controlled gel delivery unit, which supplies the quantity for the actuation of the control valve.
  • Oil delivery unit also includes an auxiliary pump, which supplies the hydraulic quantity to act on the quick-closing valve, as well as for the electro-hydraulic valve and for the adjusting cylinder of the adjusting unit of the pump.
  • the energy consumption of the unit is minimal because the variable displacement pump only supplies the quantity and pressure required by the control valve.
  • the electrohydraulic actuator for turbine valves essentially consists of a hydraulic supply 1, an oil delivery unit 2 and two identical drives 3, 4, which are responsible for controlling the quick-closing valve 29 and the control valve 30.
  • the auxiliary pump 15 and variable displacement pump 16 integrated in the oil delivery unit 2 deliver oil from the hydraulic tank 6 via the lines 32 and respectively. 33.
  • the auxiliary pump 15 supplies the electrohydraulic valve 10 with oil, a filter 8 being installed as an intermediate.
  • the drive 4 is also supplied with oil via the throttle 9 and line 34, whereupon the quick-closing valve 29 opens.
  • the oil flows through the throttle 22a into the piston chamber of the adjusting cylinder 21a.
  • the spring 35a is compressed; the Oe1 still present in the spring chamber can flow out to the tank 6 via the outlet 24.
  • the auxiliary pump 15 is secured against excess pressure by the pressure relief valve 7 and its outlet 24.
  • the control valve 30 While the quick-closing valve 29 opens completely, the control valve 30 must have a regulating effect on the amount of steam flowing through the steam line 26 to the turbine.
  • the variable displacement pump 16 in turn supplies the drive 3 with oil via the line 37.
  • the dynamics of the opening of the control valve 30 do not differ from that of the quick-closing valve 29, i.e. the piston chamber of the adjusting cylinder 21 is acted upon by the throttle 22, whereupon the spring 35 is compressed and the residual oil remaining therein can flow back to the tank 6 via the outlet 24.
  • the degree of opening of the control valve 30 is signaled by an electrical setpoint 27 to the electro-hydraulic valve 10.
  • the adjustment quantity entered on the adjustment cylinder 18 causes a change in the delivery quantity of the adjustment pump 16, whereupon oil is additionally applied to the piston chamber of the adjustment cylinder 21 and the control valve 30 accordingly assumes a new opening position.
  • the desired degree of opening of the control valve 30 is maintained by continuously comparing the feedback signal 28 from the feedback transmitter 5 with the setpoint 27 in the comparator 36. A resulting deviation between the setpoint and actual value is signaled to the electro-hydraulic valve 10. If the control valve 30 is too large, the control cylinder 18 closes by means of spring force.
  • the variable displacement pump 16 now delivers less accordingly; the excess oil from the actuating cylinder 18 flows to the electro-hydraulic valve 10 and from there via the outlet 24 back to the tank.
  • the control valve 30 When the control valve 30 is completely open, the maximum defined by the pressure relief valve 11 is established Pressure, wherein the set pressure of the pressure relief valve 11 is at least the sum of the pressure force and the spring force of the adjusting cylinder 21.
  • the control valve spindle is therefore constantly loaded.
  • the directional control valve 13 In order to prevent this permanent heavy load, the directional control valve 13 is switched and the pressure is reduced by the limit switch on the control valve 30, in its fully open position, until the pressure corresponds to the value defined in the pressure relief valve 14.
  • a filter 12 is installed in front of the directional control valve 13 in the outflow direction.
  • the outflow amplifier 19 switches on and opens. Via the bypass line 31, the oil under pressure in the piston chamber flows into the spring chamber of the adjusting cylinder 21 and from there via the outlet 24 back into the tank 6. This prevents the pump and lines from having to swallow large amounts of oil during these load changes. So that the pumps 15, 16 can deliver a minimum amount of oil which is advantageous for their cooling during operation under constant load, the throttles 23, 23a are provided, which ensure this recirculation.
  • the two-way valves 20, 20a open, controlled by the electrical signals 38, 38a.
  • the drain amplifiers 19, 19a also open.
  • the oil can thus suddenly escape from the piston spaces via the bypass lines 31, 31a in the spring spaces of the adjusting cylinders 21, 21a and flow out from here through the already opened two-way valves 20, 20a 24.
  • Information aimed at closing is simultaneously via the electrical setpoint 27 brought up. The delivery of the pumps 15, 16 drops to zero.

Abstract

Der elektrohydraulische Stellantrieb für Turbinenventile umfasst im wesentlichen ein Stellventil (30), ein Schnellschlussventil (29), eine Hydraulikversorgung (1) und eine Oelförderungseinheit (2). Um einen hydraulischen Antrieb für Turbinenventile zu schaffen, der einerseits den hohen Anforderungen hinsichtlich Stellkraft und Stellgeschwindigkeit genügt und andererseits die mit der Uebertragung hydraulischer Energie zusammenhängenden Probleme vermeidet, wird pro Turbineneinlassventil je mindestens ein Stellventil (30) und mindestens ein Schnellschlussventil (29) zugeordnet. Die Antriebe (3, 4) dieser beiden Ventile (29, 30) sind gleicher Ausführung und untereinander austauschbar, und werden zu einer am Ventilgehäuse angeordneten kompakten Antriebseinheit integriert. Dabei sind die Antriebe (3, 4) paarweise mit einer unmittelbar daneben angeordneten Hydraulikversorgung (1) angeschlossen. Ferner werden die Antriebe (3, 4) von einer mit der Hydraulikversorgung (1) integrierten volumetrisch geregelten Oelförderungseinheit (2) gesteuert, wobei diese eine Verstellpumpe (16) zur Steuerung des Stellventils (30) und eine Hilfspumpe (15) zur Steuerung des Schnellschlussventils (29) beinhaltet.The electrohydraulic actuator for turbine valves essentially comprises a control valve (30), a quick-closing valve (29), a hydraulic supply (1) and an oil delivery unit (2). In order to create a hydraulic drive for turbine valves that on the one hand meets the high requirements with regard to actuating force and actuating speed and on the other hand avoids the problems associated with the transmission of hydraulic energy, at least one control valve (30) and at least one quick-acting valve (29) are assigned to each turbine inlet valve. The drives (3, 4) of these two valves (29, 30) are of the same design and interchangeable, and are integrated into a compact drive unit arranged on the valve housing. The drives (3, 4) are connected in pairs with a hydraulic supply (1) arranged directly next to them. Furthermore, the drives (3, 4) are controlled by a volumetrically regulated oil delivery unit (2) integrated with the hydraulic supply (1), this unit having a variable displacement pump (16) for controlling the control valve (30) and an auxiliary pump (15) for controlling the quick-closing valve (29) includes.

Description

Die Erfindung betrifft einen elektrohydraulischen Stellantrieb für Turbinenventile gemäss Oberbegriff des Patentanspruchs.The invention relates to an electro-hydraulic actuator for turbine valves according to the preamble of the claim.

Im Turbinenbau erfolgt die Versorgung der Stellantriebe der einzelnen Turbinenventile mit hydraulischer Energie stets über ein zentrales hydraulisches Versorgungssystem, welches einen zentralen Hydraulikflüssigkeitsbehälter und meistens mehrere gegen hydraulische Druckspeicher arbeitende Flüssigkeitspumpen umfasst. Für die Verbindung eines Stellantriebes mit dem zentralen hydraulischen Versorgungssystem sind demnach jeweils mindestens zwei Rohrleitungen erforderlich, wobei die eine Rohrleitung die Versorgung des Stellantriebes mit unter Druck stehenden Hydraulikflüssigkeit übernimmt, während die andere Rohrleitung die bei einer Entlastung der hydraulischen Bauteile ablaufende Hydraulikflüssigkeit in den zentralen Hydraulikflüssigkeitsbehälter zurückführt. Um schmutzunempfindlichere Stellantriebe zu erhalten, arbeitet man vorteilhaft mit relativ tiefen Betriebsdrücken.; dies hat allerdings zur Folge, dass grosse Oeltanks vorgesehen werden müssen.In turbine construction, the actuators of the individual turbine valves are always supplied with hydraulic energy via a central hydraulic supply system, which comprises a central hydraulic fluid reservoir and usually several fluid pumps working against hydraulic pressure accumulators. Accordingly, at least two pipes are required for connecting an actuator to the central hydraulic supply system, one pipe taking care of supplying the actuator with pressurized hydraulic fluid, while the other pipeline feeds the hydraulic fluid that flows when the hydraulic components are relieved into the central hydraulic fluid reservoir leads back. In order to obtain actuators that are less sensitive to dirt, it is advantageous to work with relatively low operating pressures .; however, this means that large oil tanks have to be provided.

Will man von einem zentralen hydraulischen Versorgungssystem alle Stellantriebe einer Turbine bedienen, so weist die Anlage zwangsläufig viele lange Oelleitungen auf. Um die Uebertragungssicherheit der hydraulischen Energie zu gewährleisten, erfordern diese Rohrleitungen einen erheblichen Aufwand für Planung, Konstruktion, Qualitätssicherung und Wartung. Ausser Druckschwingungen und Druckspitzen in langen Leitungen ist insbesondere auch die Beanspruchung durch Wärmedehnungen zu berücksichtigen. Schliesslich muss auch noch aus Sicherheitsgründen die von einem Bruch der Leitungen im Warmbereich ausgehende Brandgefahr berücksichtigt werden. Wohl liesse sich im Interesse des Brandschutzes die Brandgefahr durch den Einsatz doppelwandiger Rohre reduzieren, allein bringt dies hinsichtlich Verlegung und Zugänglichkeit erhebliche Probleme mit sich. Hinsichtlich Brandschutzes kann der Einsatz von schwer brennbaren Hydraulikflüssigkeiten erwogen werden. Derartige Hydraulikflüssigkeiten sind jedoch kostspielig, erfordern auf Grund ihrer geringen Alterungsstabilität eine Regenerieranlage, die Instruktionen der Lieferanten müssen genauestens beachtet werden und sind gegenüber Wärmeeinwirkungen sehr zersetzungsgefährdet.If you want to operate all the actuators of a turbine from a central hydraulic supply system, the system inevitably has many long oil lines. In order to ensure the transmission security of the hydraulic energy, these pipelines require considerable effort for planning, construction, quality assurance and maintenance. In addition to pressure fluctuations and pressure peaks in long lines, the stress caused by thermal expansion must also be taken into account. Finally, for safety reasons, the risk of fire from a broken pipe in the warm area must also be taken into account. In the interest of fire protection, the risk of fire could be reduced by using double-walled pipes, but this alone causes considerable problems with regard to laying and accessibility. With regard to fire protection, the use of flame-resistant hydraulic fluids can be considered. However, such hydraulic fluids are expensive, require a regeneration system due to their low aging stability, the instructions of the suppliers must be followed carefully and are very susceptible to decomposition when exposed to heat.

Die in den EP 0 040 732 Al und EP 0 040 737 Al bekanntgegebenen Lösungen vermeiden die oben beschriebenen Nachteile, indem durch die Integration des hydraulischen Versorgungssystem in den Stellantrieb die bisher erforderlichen Hydraulikzuleitungen und der mit diesen Leitungen verbundene Aufwand entfallen können.The solutions disclosed in EP 0 040 732 A1 and EP 0 040 737 A1 avoid the disadvantages described above, since the hydraulic supply lines previously required and the effort associated with these lines can be eliminated by integrating the hydraulic supply system into the actuator.

Diese Anordnung weist jedoch Nachteile auf:

  • a) Für jeden Stellantrieb muss ein eigenes hydraulisches Versorgungssystem zugeordnet werden. Bei der Vielzahl von Schnellschluss- und Stellventilen einer Turbine ist dementsprechend eine gleich grosse Zahl hydraulischer Versorgungssysteme vorzusehen; entsprechend gross ist auch der finanzielle Aufwand.
  • b) Da das jeweilige hydraulische Versorgungssystem eine autonome Einheit bildet, muss bei Ausfall der Flüssigkeitspumpe eine zweite zuschaltbare Flüssigkeitspumpe vorgesehen werden, welche von einem zweiten Elektromotor angetrieben ist. Durch diese Massnahme wird zwar die Betriebssicherheit des Stellantriebes erhöht, allerdings muss dabei eine entsprechende Vergrösserung des Bauvolumens und der Kosten des hydraulischen Versorgungssystems in Kauf genommen werden.
  • c) Aus denselben Ueberlegungen wie unter b) muss der hydraulische Druckspeicher in mindestens zwei Teilspeicher unterteilt werden, wobei das Speichervolumen der Teilspeicher derart bemessen ist, dass auch bei Ausfall eines Teilspeichers eine für die Betätigung des hydraulischen Stellzylinders ausreichend Hydraulikflüssigkeitsmenge verfügbar ist. Die daraus resultierende Konsequenz ist auch hier eine Vergrösserung des Bauvolumens und der Kosten des hydraulischen Versorgungssystems.
  • d) Aus obigen Ueberlegungen ist es deshalb fraglich, ob die angestrebte Minimierung des Bauvolumens des hydraulischen Versorgungssystems - soweit dieses mit dem Stellantrieb zu einem am Ventilgehäuse angeordneten kompakten Antriebsblock integriert werden kann - im vorgestellten Rahmen überhaupt machbar ist.
  • e) Darüber hinaus verpflanzen sich die von den Ventilen bei Betrieb ausgehenden Vibrationen, insbesondere bei kurzfristig einander folgenden Lastwechseln, auf die relativ empfindlichen Elemente der Hydraulikversorgung fort. Die Lebensdauer dieser Elemente nimmt ab; Störungen des Betriebes sind die Folge.
However, this arrangement has disadvantages:
  • a) A separate hydraulic supply system must be assigned to each actuator. Given the large number of quick-closing and control valves in a turbine, an equal number of hydraulic supply systems must be provided accordingly; the financial outlay is correspondingly large.
  • b) Since the respective hydraulic supply system forms an autonomous unit, a second switchable liquid pump which is driven by a second electric motor must be provided if the liquid pump fails. Although this measure increases the operational safety of the actuator, a corresponding increase in the construction volume and the costs of the hydraulic supply system must be accepted.
  • c) For the same considerations as under b), the hydraulic pressure accumulator must be divided into at least two partial accumulators, the accumulator volume of the partial accumulators being dimensioned such that even if one partial accumulator fails, a sufficient quantity of hydraulic fluid is available for actuating the hydraulic actuating cylinder. The resulting consequence is an increase in the construction volume and the costs of the hydraulic supply system.
  • d) From the above considerations, it is therefore questionable whether the desired minimization of the construction volume of the hydraulic supply system - insofar as this can be integrated with the actuator to form a compact drive block arranged on the valve housing - is feasible within the scope presented.
  • e) In addition, the vibrations emanating from the valves during operation, especially in the event of load changes which follow one another for a short time, propagate to the relatively sensitive elements of the hydraulic supply. The lifespan of these elements decreases; Disruptions to operation are the result.

Aufgabe der Erfindung ist es, die vorgenannten Nachteile zu beheben und einen elektrohydraulischen Stellantrieb für Turbinenventile zu schaffen, der einerseits den hohen Anforderungen hinsichtlich Stellkraft und Stellgeschwindigkeit genügt und andererseits die mit der Uebertragung hydraulischer Energie zusammenhängenden Probleme vermeidet.The object of the invention is to eliminate the aforementioned disadvantages and an electro-hydraulic actuator for turbine valves, which on the one hand meets the high requirements with regard to actuating force and actuating speed and on the other hand avoids the problems associated with the transmission of hydraulic energy.

Der zur Lösung der genannten Aufgabe erfindungsgemäss vorgeschlagene elektrohydraulische Stellantrieb für Turbinenventile ist dadurch gekennzeichnet, dass pro Turbineneinlassventil je mindestens ein Stellventil und mindestens ein Schnellschlussventil zugeordnet sind, deren Antriebe gleicher Ausführung und zu einem am Ventilgehäuse angeordneten kompakten Antriebseinheit integriert sind, wobei diese Antriebe paarweise mit einer unmittelbar daneben angeordneten Hydraulikversorgung angeschlossen und von einer mit der Hydraulikversorgung integrierten vblumetrisch geregelten Oelförderungseinheit gesteuert sind.The electrohydraulic actuator for turbine valves proposed according to the invention to achieve the stated object is characterized in that at least one control valve and at least one quick-closing valve are assigned to each turbine inlet valve, the drives of the same design and integrated into a compact drive unit arranged on the valve housing, these drives being paired with connected directly to a hydraulic supply and are controlled by a vblumetrically controlled oil delivery unit integrated with the hydraulic supply.

Die Vorteile der Erfindung sind im wesentlichen darin zu sehen, dass durch die vorgeschlagene Lösung der Anbau je eines Stell- und Schnellschlussventils an jedem Turbineneinlassventil, vom benötigten und von dem zur Verfügung stehenden Platz her betrachtet, problemlos bewerkstelligt werden kann. Dadurch, dass die beiden Antriebe gleicher Ausführung sind, ist der Grad der Austauschbarkeit grösstmöglich erreicht.The advantages of the invention are to be seen essentially in the fact that the proposed solution enables the installation of one control and one quick-closing valve on each turbine inlet valve, from the required space and from the available space, without any problems. The fact that the two drives are of the same design means that the degree of interchangeability has been achieved as far as possible.

Ein weiterer Vorteil der Erfindung ist darin zu sehen, dass eine Hydraulikversorgung je ein Stell- und Schnellschlussventil bedient. Dadurch, dass die Hydraulikversorgung platzmässig nicht mehr konditioniert ist, kann sie robuster, einfacher und billiger gebaut werden.Another advantage of the invention can be seen in the fact that a hydraulic supply operates one control valve and one quick-closing valve. Because the hydraulic supply is no longer conditioned in terms of space, it can be made more robust, simpler and cheaper.

Ein Vorteil der Erfindung ist des weiteren darin zu sehen, dass die Hydraulikversorgung eine volumetrisch geregelte Gelförderungseinheit beinhaltet, welche die Menge für die Beaufschlagung des Stellventils liefert. Zu dieser Oelförderungseinheit gehört auch eine Hilfspumpe, welche die Hydraulikmenge zur Beaufschlagung des Schnellschlussventils sowie für das elektrohydraulische Ventil und für den Verstellzylinder der Verstelleinheit der Pumpe liefert. Der Energieverbrauch der Einheit wird minimal, denn die Verstellpumpe liefert nur jene Menge und den Druck, die vom Stellventil benötigt werden.Another advantage of the invention can be seen in the fact that the hydraulic supply includes a volumetrically controlled gel delivery unit, which supplies the quantity for the actuation of the control valve. To this Oil delivery unit also includes an auxiliary pump, which supplies the hydraulic quantity to act on the quick-closing valve, as well as for the electro-hydraulic valve and for the adjusting cylinder of the adjusting unit of the pump. The energy consumption of the unit is minimal because the variable displacement pump only supplies the quantity and pressure required by the control valve.

Anhand der Zeichnung sind Aufbau und Wirkungsweise eines Ausführungsbeispiels der Erfindung schematisch dargestellt und näher erläutert.Based on the drawing, the structure and mode of operation of an embodiment of the invention are shown schematically and explained in more detail.

Es zeigt:

  • Fig. 1 Elektrohydraulischer Stellantrieb für Turbinenventile für Stell- und Schnellschlussventil.
It shows:
  • Fig. 1 electrohydraulic actuator for turbine valves for control and quick-closing valve.

Wie aus Fig. 1 ersichtlich ist, besteht der elektrohydraulische Stellantrieb für Turbinenventile im wesentlichen aus einer Hydraulikversorgung 1, einer Oelförderungseinheit 2 und aus zwei gleichen Antrieben 3, 4, welche für die Steuerung des Schnellschlussventils 29 und Stellventils 30 verantwortlich sind. Mit dem Start des Motors 17 fördern die der Oelförderungseinheit 2 integrierten Hilfspumpe 15 und Verstellpumpe 16 Oel aus dem Hydrauliktank 6 über die Leitungen 32 resp. 33. Die Hilfspumpe 15 versorgt das elektrohydraulische Ventil 10 mit Oel, wobei intermediär ein Filter 8 eingebaut ist. Zugleich wird der Antrieb 4 über die Drossel 9 und Leitung 34 auch mit Oel versorgt, worauf das Schnellschlussventil 29 öffnet. Hierzu fliesst das Oel durch die Drossel 22a in den Kolbenraum des Verstellzylinders 21a. Die Feder 35a wird zusammengedrückt; das in der Federkammer noch vorhandene Oe1 kann über den Ablauf 24 zum Tank 6 abfliessen. Die Sicherung der Hilfspumpe 15 gegen Ueberdruck wird vom Druckbegrenzungsventil 7 und dessen Ablauf 24 übernommen.As can be seen from FIG. 1, the electrohydraulic actuator for turbine valves essentially consists of a hydraulic supply 1, an oil delivery unit 2 and two identical drives 3, 4, which are responsible for controlling the quick-closing valve 29 and the control valve 30. With the start of the engine 17, the auxiliary pump 15 and variable displacement pump 16 integrated in the oil delivery unit 2 deliver oil from the hydraulic tank 6 via the lines 32 and respectively. 33. The auxiliary pump 15 supplies the electrohydraulic valve 10 with oil, a filter 8 being installed as an intermediate. At the same time, the drive 4 is also supplied with oil via the throttle 9 and line 34, whereupon the quick-closing valve 29 opens. For this purpose, the oil flows through the throttle 22a into the piston chamber of the adjusting cylinder 21a. The spring 35a is compressed; the Oe1 still present in the spring chamber can flow out to the tank 6 via the outlet 24. The auxiliary pump 15 is secured against excess pressure by the pressure relief valve 7 and its outlet 24.

Während das Schnellschlussventil 29 ganz öffnet, muss das Stellventil 30 auf die durch die Dampfleitung 26 zur Turbine strömende Dampfmenge regulierend einwirken können. Die Verstellpumpe 16 versorgt ihrerseits über die Leitung 37 den Antrieb 3 mit Oel. Die Dynamik des Oeffnens des Stellventils 30 unterscheidet sich nicht von derjenigen des Schnellschlussventils 29, d.h. der Kolbenraum des Verstellzylinders 21 wird über die Drossel 22 beaufschlagt, worauf die Feder 35 zusammengedrückt wird und das darin verbliebene Restöl über den Ablauf 24 zum Tank 6 rückfliessen kann.While the quick-closing valve 29 opens completely, the control valve 30 must have a regulating effect on the amount of steam flowing through the steam line 26 to the turbine. The variable displacement pump 16 in turn supplies the drive 3 with oil via the line 37. The dynamics of the opening of the control valve 30 do not differ from that of the quick-closing valve 29, i.e. the piston chamber of the adjusting cylinder 21 is acted upon by the throttle 22, whereupon the spring 35 is compressed and the residual oil remaining therein can flow back to the tank 6 via the outlet 24.

Der Grad der Oeffnung des Stellventils 30 wird von einem elektrischen Sollwert 27 dem elektrohydraulischen Ventil 10 signalisiert. Die auf den Verstellzylinder 18 eingegebene Verstellgrösse bewirkt eine Förderungsmengenänderung der Verstellpumpe 16, worauf der Kolbenraum des Stellzylinders 21 zusätzlich mit Oel beaufschlagt wird und das Stellventil 30 infolgedessen entsprechend eine neue Oeffnungsposition einnimmt. Der gewollte Oeffnungsgrad des Stellventils 30 wird eingehalten, indem im Vergleichsglied 36 das aus dem Rückführgeber 5 stammende Rückführsignal 28 mit dem Sollwert 27 ständig verglichen wird. Eine hieraus resultierende Abweichung zwischen Soll- und Istwert wird dem elektrohydraulischen Ventil 10 signalisiert. Bei zu grosser Oeffnung des Stellventils 30 schliessE der Stellzylinder 18 mittels Federkraft. Die Verstellpumpe 16 fördert nun entsprechend weniger; das aus dem Stellzylinder 18 überschüssige Oel fliesst zum elektrohydraulischen Ventil 10 und von hier über den Ablauf 24 zum Tank zurück.The degree of opening of the control valve 30 is signaled by an electrical setpoint 27 to the electro-hydraulic valve 10. The adjustment quantity entered on the adjustment cylinder 18 causes a change in the delivery quantity of the adjustment pump 16, whereupon oil is additionally applied to the piston chamber of the adjustment cylinder 21 and the control valve 30 accordingly assumes a new opening position. The desired degree of opening of the control valve 30 is maintained by continuously comparing the feedback signal 28 from the feedback transmitter 5 with the setpoint 27 in the comparator 36. A resulting deviation between the setpoint and actual value is signaled to the electro-hydraulic valve 10. If the control valve 30 is too large, the control cylinder 18 closes by means of spring force. The variable displacement pump 16 now delivers less accordingly; the excess oil from the actuating cylinder 18 flows to the electro-hydraulic valve 10 and from there via the outlet 24 back to the tank.

Die Sicherung der Verstellpumpe 16 gegen Ueberdruck wird vom Druckbegrenzungsventil 11 und dessen Ablauf 24 übernommen.Securing the variable displacement pump 16 against excess pressure is carried out by the pressure relief valve 11 and its outlet 24.

Wenn das Stellventil 30 ganz offen ist, stellt sich der durch das Druckbegrenzungsventil 11 definierte maximale Druck ein, wobei der eingestellte Druck des Druckbegrenzungsventils 11 mindestens die Summe aus Druckkraft und Federkraft des Verstellzylinders 21 ist. Die Stellventilspindel ist somit dauernd belastet. Um diese dauernde starke Belastung zu verhüten, wird über nicht eingezeichnete Endschalter am Stellventil 30, bei dessen voll offener Lage, das Wegeventil 13 geschaltet und der Druck soweit abgesenkt, bis er mit dem im Druckbegrenzungsventil 14 definierten Wert übereinstimmt.When the control valve 30 is completely open, the maximum defined by the pressure relief valve 11 is established Pressure, wherein the set pressure of the pressure relief valve 11 is at least the sum of the pressure force and the spring force of the adjusting cylinder 21. The control valve spindle is therefore constantly loaded. In order to prevent this permanent heavy load, the directional control valve 13 is switched and the pressure is reduced by the limit switch on the control valve 30, in its fully open position, until the pressure corresponds to the value defined in the pressure relief valve 14.

Das überschüssige Oel wird über den Ablauf 24 in den Tank 6 zurückgeführt. Vor dem Wegeventil 13 in Abströmungsrichtung ist noch ein Filter 12 eingebaut.The excess oil is returned to the tank 6 via the outlet 24. A filter 12 is installed in front of the directional control valve 13 in the outflow direction.

Bei schnellen Lastabsenkungen der Turbine schaltet der Abflussverstärker 19 ein und macht auf. Ueber die Bypassleitung 31 fliesst das im Kolbenraum unter Druck stehende Oel in den Federraum des Verstellzylinders 21 und von hier über den Ablauf 24 in den Tank 6 zurück. Dadurch vermeidet man, dass Pumpe und Leitungen bei diesen Laständerungen grosse Mengen Oel schlucken müssen. Damit die Pumpen 15, 16 während des Betriebes bei konstanter Last eine zu ihrer Kühlung vorteilhafte minimale Oelmenge fördern können, sind die Drosseln 23, 23a vorgesehen, welche ebendiese Rezirkulation gewährleisten.When the load on the turbine drops rapidly, the outflow amplifier 19 switches on and opens. Via the bypass line 31, the oil under pressure in the piston chamber flows into the spring chamber of the adjusting cylinder 21 and from there via the outlet 24 back into the tank 6. This prevents the pump and lines from having to swallow large amounts of oil during these load changes. So that the pumps 15, 16 can deliver a minimum amount of oil which is advantageous for their cooling during operation under constant load, the throttles 23, 23a are provided, which ensure this recirculation.

Bei Schnellschluss machen die Zweiwegeventile 20, 20a, gesteuert durch die elektrischen Signale 38, 38a, auf. Ebenfalls machen die Abflussverstärker 19, 19a auf. Das Oel kann somit aus den Kolbenräumen über die Bypassleitungen 31, 31a schlagartig in den Federräumen der Verstellzylinder 21, 21a entweichen und von hier durch die bereits geöffneten Zweiwegeventile 20, 20a abfliessen 24. Eine auf Schliessung gerichtete-Information wird gleichzeitig über den elektrischen Sollwert 27 herangetragen. Die Förderung der Pumpen 15, 16 geht auf Null zurück.In the event of a quick close, the two-way valves 20, 20a open, controlled by the electrical signals 38, 38a. The drain amplifiers 19, 19a also open. The oil can thus suddenly escape from the piston spaces via the bypass lines 31, 31a in the spring spaces of the adjusting cylinders 21, 21a and flow out from here through the already opened two-way valves 20, 20a 24. Information aimed at closing is simultaneously via the electrical setpoint 27 brought up. The delivery of the pumps 15, 16 drops to zero.

Claims (1)

Elektrohydraulischer Stellantrieb für Turbinenventile im wesentlichen bestehend aus einem Stellventil, einem Schnellschlussventil und einer Hydraulikversorgung, dadurch gekennzeichnet, dass pro Turbineneinlassventil je mindestens ein Stellventil (30) und mindestens ein Schnellschluss- - ventil (29) zugeordnet sind, deren Antriebe (3, 4) gleicher Ausführung und zu einer am Ventilgehäuse angeordneten kompakten Antriebseinheit integriert sind, wobei diese Antriebe (3, 4) paarweise mit einer unmittelbar daneben angeordneten Hydraulikversorgung (I) angeschlossen und von einer mit der Hydraulikversorgung (1) integrierten volumetrisch geregelten Oelförderungseinheit (2) gesteuert sind.Electrohydraulic actuator for turbine valves essentially consisting of a control valve, a quick-closing valve and a hydraulic supply, characterized in that at least one control valve (30) and at least one quick-closing valve (29) are assigned to each turbine inlet valve, the drives (3, 4) of which same design and integrated into a compact drive unit arranged on the valve housing, these drives (3, 4) being connected in pairs with a hydraulic supply (I) arranged directly next to them and being controlled by a volumetrically controlled oil delivery unit (2) integrated with the hydraulic supply (1) .
EP84105238A 1983-05-30 1984-05-09 Electro-hydraulic actuator for turbine valves Expired EP0127027B1 (en)

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CH295583 1983-05-30
CH2955/83 1983-05-30

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US (1) US4589444A (en)
EP (1) EP0127027B1 (en)
JP (1) JPS59231108A (en)
CS (1) CS244819B2 (en)
DE (1) DE3469777D1 (en)
PL (1) PL145034B1 (en)
YU (1) YU43361B (en)

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EP0419946A1 (en) * 1989-09-28 1991-04-03 Asea Brown Boveri Ag Valve motor
EP0430089A1 (en) * 1989-12-01 1991-06-05 Asea Brown Boveri Ag Actuator
EP0451543A1 (en) * 1990-04-09 1991-10-16 Asea Brown Boveri Ag Actuation system for a steam regulating valve
EP0462387A1 (en) * 1990-06-18 1991-12-27 Asea Brown Boveri Ag Hydraulic control and safety system
US5269141A (en) * 1990-06-18 1993-12-14 Asea Brown Boveri Ltd. Hydraulic safety and regulating system
DE19636746A1 (en) * 1996-09-10 1998-03-12 Siemens Ag Valve arrangement for turbine
ITMI20082339A1 (en) * 2008-12-30 2010-06-30 Ansaldo Energia Spa PLANT FOR THE PRODUCTION OF ELECTRICITY
CN103511004A (en) * 2013-09-17 2014-01-15 上海新力机器厂 Closed electro-hydraulic actuator and assembly of closed electro-hydraulic actuator
WO2016096222A1 (en) * 2014-12-19 2016-06-23 Voith Patent Gmbh Actuating drive for a control valve, in particular steam turbine control valve and method for operating same
WO2016096221A1 (en) * 2014-12-19 2016-06-23 Voith Patent Gmbh Actuating drive for a control valve, in particular a steam turbine control valve, and method for operating same
WO2017021080A1 (en) * 2015-07-31 2017-02-09 Voith Patent Gmbh Hydraulic drive for executing a linear movement
WO2017071912A1 (en) * 2015-10-30 2017-05-04 Siemens Aktiengesellschaft Turbine with quick-closing valves and regulating valves
CN109404065A (en) * 2018-10-12 2019-03-01 上海华电电力发展有限公司 Prevent host porthole blocking solenoid valve failure from causing the control method of unit tripping
CN111566357A (en) * 2017-12-21 2020-08-21 穆格股份有限公司 Actuating drive with hydraulic drainage booster

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DE10058560A1 (en) * 2000-11-24 2002-06-13 Voith Turbo Kg Electro-hydraulic actuator
DE102004042891B3 (en) * 2004-08-31 2005-10-06 Hydac System Gmbh Safety circuit for media-powered consumers and method of operation thereof
CN101629496B (en) * 2009-07-30 2011-08-17 杭州和利时自动化有限公司 Digital electrohydraulic control system of steam turbine with isolated network operation
CN102922771A (en) * 2012-11-19 2013-02-13 无锡市京锡冶金液压机电有限公司 Connecting method of load control dual-pressure system for high-speed punching machine
CN102950804A (en) * 2012-11-19 2013-03-06 无锡市京锡冶金液压机电有限公司 High-speed punch hydraulic system connection method capable of realizing fast direction change
JP6352781B2 (en) * 2014-11-26 2018-07-04 三菱日立パワーシステムズ株式会社 Hydraulic drive device for steam valve, combined steam valve and steam turbine
WO2020198599A1 (en) * 2019-03-27 2020-10-01 Salvatore Shifrin Self contained hydraulic lock apparatus
JP7227845B2 (en) * 2019-05-14 2023-02-22 株式会社東芝 Steam valve drive system, steam valve system and steam turbine plant
CN110345113A (en) * 2019-08-13 2019-10-18 国电浙江北仑第一发电有限公司 A kind of power station Bypass Control oil pressure charging system

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CH678968A5 (en) * 1989-09-28 1991-11-29 Asea Brown Boveri
US5193779A (en) * 1989-09-28 1993-03-16 Asea Brown Boveri Ltd. Actuating drive
EP0419946A1 (en) * 1989-09-28 1991-04-03 Asea Brown Boveri Ag Valve motor
US5137253A (en) * 1989-12-01 1992-08-11 Asea Brown Boveri Ltd. Actuator
EP0430089A1 (en) * 1989-12-01 1991-06-05 Asea Brown Boveri Ag Actuator
US5095804A (en) * 1990-04-09 1992-03-17 Asea Brown Boveri Ltd. Drive for a steam servo valve
EP0451543A1 (en) * 1990-04-09 1991-10-16 Asea Brown Boveri Ag Actuation system for a steam regulating valve
CH681380A5 (en) * 1990-04-09 1993-03-15 Asea Brown Boveri
EP0462387A1 (en) * 1990-06-18 1991-12-27 Asea Brown Boveri Ag Hydraulic control and safety system
US5269141A (en) * 1990-06-18 1993-12-14 Asea Brown Boveri Ltd. Hydraulic safety and regulating system
CH683017A5 (en) * 1990-06-18 1993-12-31 Asea Brown Boveri An electrohydraulic actuator.
DE19636746A1 (en) * 1996-09-10 1998-03-12 Siemens Ag Valve arrangement for turbine
ITMI20082339A1 (en) * 2008-12-30 2010-06-30 Ansaldo Energia Spa PLANT FOR THE PRODUCTION OF ELECTRICITY
EP2204551A1 (en) * 2008-12-30 2010-07-07 Ansaldo Energia S.p.A. Gas turbine for electric power generation
CN103511004A (en) * 2013-09-17 2014-01-15 上海新力机器厂 Closed electro-hydraulic actuator and assembly of closed electro-hydraulic actuator
CN103511004B (en) * 2013-09-17 2015-05-13 上海新力机器厂 Closed electro-hydraulic actuator and assembly of closed electro-hydraulic actuator
US10400799B2 (en) 2014-12-19 2019-09-03 Voith Patent Gmbh Actuating drive for a control valve, in particular a steam turbine control valve, and method for operating same
WO2016096222A1 (en) * 2014-12-19 2016-06-23 Voith Patent Gmbh Actuating drive for a control valve, in particular steam turbine control valve and method for operating same
WO2016096221A1 (en) * 2014-12-19 2016-06-23 Voith Patent Gmbh Actuating drive for a control valve, in particular a steam turbine control valve, and method for operating same
CN107109961B (en) * 2014-12-19 2020-02-14 福伊特专利有限公司 Actuating drive for a control valve, in particular a steam turbine control valve, and method for operating the actuating drive
CN107109961A (en) * 2014-12-19 2017-08-29 福伊特专利有限公司 For regulating valve, the especially servo drive of steam turbine regulating valve and its operation method
US10578227B2 (en) 2015-07-31 2020-03-03 Voith Patent Gmbh Hydraulic drive for executing a linear movement
WO2017021080A1 (en) * 2015-07-31 2017-02-09 Voith Patent Gmbh Hydraulic drive for executing a linear movement
WO2017071912A1 (en) * 2015-10-30 2017-05-04 Siemens Aktiengesellschaft Turbine with quick-closing valves and regulating valves
US10900375B2 (en) 2015-10-30 2021-01-26 Siemens Aktiengesellschaft Turbine with quick-closing valves and regulating valves
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
CN109404065A (en) * 2018-10-12 2019-03-01 上海华电电力发展有限公司 Prevent host porthole blocking solenoid valve failure from causing the control method of unit tripping

Also Published As

Publication number Publication date
PL145034B1 (en) 1988-07-30
US4589444A (en) 1986-05-20
CS244819B2 (en) 1986-08-14
CS394484A2 (en) 1985-08-15
DE3469777D1 (en) 1988-04-14
EP0127027B1 (en) 1988-03-09
JPH0472042B2 (en) 1992-11-17
JPS59231108A (en) 1984-12-25
PL247906A1 (en) 1985-03-12
YU85884A (en) 1987-12-31
YU43361B (en) 1989-06-30

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