EP1191190A1 - Method for regulating a steam turbine and steam turbine - Google Patents

Method for regulating a steam turbine and steam turbine Download PDF

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Publication number
EP1191190A1
EP1191190A1 EP00120574A EP00120574A EP1191190A1 EP 1191190 A1 EP1191190 A1 EP 1191190A1 EP 00120574 A EP00120574 A EP 00120574A EP 00120574 A EP00120574 A EP 00120574A EP 1191190 A1 EP1191190 A1 EP 1191190A1
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EP
European Patent Office
Prior art keywords
control
valves
steam turbine
valve
steam
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.)
Withdrawn
Application number
EP00120574A
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German (de)
French (fr)
Inventor
Heinrich Dr. Oeynhausen
Richard Steinborn
Heribert Werthes
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Siemens AG
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Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP00120574A priority Critical patent/EP1191190A1/en
Priority to ES01983470T priority patent/ES2344591T3/en
Priority to CNB018159753A priority patent/CN100335751C/en
Priority to DE50115502T priority patent/DE50115502D1/en
Priority to JP2002529646A priority patent/JP4695822B2/en
Priority to PCT/EP2001/010358 priority patent/WO2002025067A1/en
Priority to EP01983470A priority patent/EP1319117B1/en
Publication of EP1191190A1 publication Critical patent/EP1191190A1/en
Withdrawn legal-status Critical Current

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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
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves 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
    • F01D17/10—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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/05—Purpose of the control system to affect the output of the engine

Definitions

  • the invention relates to a method for controlling a Steam turbine, where the steam of the steam turbine over at least three valves is supplied.
  • the invention further relates to a steam turbine with a valve group for controlling the Steam inlet.
  • a method for regulating a steam turbine emerges the article "Practical design of speed and power controllers for steam turbines "by Johannes Dastych and Heinz Unbehauen, Martin Bennauer and Heribert Werthes, ATP 41 (1999), No. 5.
  • a steam turbine is based on speed or Performance regulated.
  • the control loop for speed and power according to figure 2 consists of function blocks such as speed / Capacity controller (D- / LR), live steam control valve (FD-STV), Interception control valve (AF-STV), steam generator (DE) and turbine (T) as well as elementary blocks, e.g. Constant, ramp and Jump function for the input signals.
  • the turbo set is powered by steam from one Steam generator supplied, the steam supply via control valves is regulated so that the necessary performance is available stands.
  • the speed and the power are regulated via a common speed / power controller both for load operation with selectable statics as well as for regulation the speed at idle.
  • the output signal of the speed / power controller acts on the live steam and interception control valves.
  • Such a regulation of a steam turbine requires a very complex control loop and control valves that allow a sufficiently quick regulation. So far only hydraulically driven control valves for Steam inlet control used because only such hydraulic drive a sufficiently quick setting valve lift is possible.
  • An actuator for a valve of a steam turbine with one Electromotive drive is known from WO98 / 13633.
  • Such an electric motor drive is particularly inexpensive and also reduces the risk of fire by avoiding it the use of hydraulic oil.
  • Such an electromotive Drive for a steam valve can be used for a Quick-closing valve of a steam turbine are used, where it is only a quick closing of the steam line arrives.
  • the electromotive are for steam turbine control
  • drives are unsuitable because they are necessary Valve stroke positions, the positioning times too short and the valve stroke settings are too imprecise.
  • the object of the invention is to provide a control method a steam turbine, which is particularly very inexpensive and also offers increased operational reliability. Another object of the invention is to provide a steam turbine with the same advantages.
  • the object is directed to a method solved by specifying a procedure for regulating a Steam turbine, where the steam of the steam turbine over at least three valves is supplied, one of the valves as one Control valve regulated and at least two valves as control valves to be controlled.
  • the configurations according to points A to F can be in any Can be combined with each other.
  • the object directed to a steam turbine is achieved according to the invention solved by specifying a steam turbine with a valve group to control the steam inlet, which valve group includes a control valve and at least two control valves.
  • the control valves preferably have an electromotive one Drive on.
  • FIG 1 shows schematically a steam turbine system.
  • one Steam turbine 1 is steam from a steam generator 3 via the Supply line 5 supplied.
  • the valve group 7 comprises a first one Control valve 9 and a second control valve 11.
  • the valve group 7 further includes a first control valve 13 and a second control valve 15.
  • Via the valve group 7, the in the steam turbine 1 regulates the amount of steam introduced. This happens depending on the one desired for the steam turbine 1 Power or speed. This is explained in more detail using the Figures 2 and 3 explained.
  • FIG. 2 shows the valve group 7 from FIG. 1 with the associated one crizungsbesciens.
  • a controller 21 generates depending from the actual value of the speed or power and the setpoint of Speed or power characterizing a controller output signal for a control difference.
  • the controller output signal is one first servo amplifier 23 of the first control valve 9 fed.
  • the controller output signal also becomes a second servo amplifier 27 of the second control valve 11 fed.
  • the Controller output signal is also a first frequency converter 25 of the first control valve 13 fed.
  • the controller output signal is also a second frequency converter 29 of the second control valve 15 fed.
  • Figure 3 shows an example of the valve lift in a diagram each of the valves 9, 11, 13, 15 depending on the controller output signal.
  • the information is in percent of the respective Maximum value shown.
  • the characteristic curve 9K gives the course of the valve lift 33 of the first regulator valve 9 in dependence from the controller output signal 31.
  • the characteristic curve 13K gives that corresponding characteristic for the first control valve 13.
  • the Characteristic 11K gives the corresponding characteristic for the second Control valve 11 on.
  • the characteristic 15K gives the corresponding one Characteristic curve for the second control valve 15.
  • the first control valve 9 opens proportional to the size of the controller output signal 31. At a value of 22.5% of the controller output signal 31 opens the first control valve 13.
  • the controller output signal 31 is the valve lift 33 for the first control valve 9 and for the first control valve 13 at 100%. From this point on, the second control valve 11 opens. At a value of 72.5%, the second control valve will eventually 15 switched on. At a value of 100% of the controller output signal 31, all valves 9, 11, 13, 15 are complete open. Starting, ramping up to nominal speed and synchronization takes place with the first control valve 9. The size of the control difference determines the opening speed of the control valves 13, 15. When there are load shedding to a negative control difference. The size of the negative control difference determines the closing speed of the control valves. Due to the lower control dynamics of the control valves, which are driven by an electric motor in the example shown the response value for a switching operation "Close" for load shedding for the control valves 9, 11 and Control valves 13, 15 may be different.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)

Abstract

The method of governing a steam turbine entails feeding steam through at least three valves, whereby one of the valves (9,11) is operated as a regulating valve and at least two (13,15) as control valves which are electric motor actuated. The valve block may comprise two regulating valves and two control valves. An Independent claim is included for a steam turbine with a valve block to control steam inlet and which comprises a regulating valve and at least two control valves.

Description

Die Erfindung betrifft ein Verfahren zur Regelung einer Dampfturbine, bei dem Dampf der Dampfturbine über mindestens drei Ventile zugeführt wird. Die Erfindung betrifft weiterhin eine Dampfturbine mit einer Ventilgruppe zur Regelung des Dampfeinlasses.The invention relates to a method for controlling a Steam turbine, where the steam of the steam turbine over at least three valves is supplied. The invention further relates to a steam turbine with a valve group for controlling the Steam inlet.

Ein Verfahren zur Regelung einer Dampfturbine geht hervor aus dem Artikel "Praxisgerechte Auslegung von Drehzahl und Leistungsreglern für Dampfturbinen" von Johannes Dastych und Heinz Unbehauen, Martin Bennauer und Heribert Werthes, ATP 41(1999), Heft 5. Eine Dampfturbine wird nach Drehzahl oder Leistung geregelt. Der Regelkreis für Drehzahl und Leistung gemäß Bild 2 besteht aus Funktionsblöcken wie Drehzahl- / Leistungsregler (D-/LR), Frischdampf-Stellventil (FD-STV), Abfangstellventil (AF-STV), Dampferzeuger (DE) und Turbine (T) sowie elementaren Blöcken, wie z.B. Konstante, Rampe und Sprungfunktion für die Eingangssignale. Zur Bereitstellung elektrischer Leistung wird der Turbosatz mit Dampf aus einem Dampferzeuger versorgt, wobei die Dampfzufuhr über Stellventile so geregelt wird, dass die notwendige Leistung zur Verfügung steht. Die Regelung der Drehzahl und der Leistung erfolgt über einen gemeinsamen Drehzahl-/Leistungsregler sowohl für den Lastbetrieb mit wählbarer Statik als auch zur Regelung der Drehzahl bei Leerlauf. Das Ausgangssignal des Drehzahl-/Leistungsreglers wirkt auf die Frischdampf- und Abfangstellventile. Eine solche Regelung einer Dampfturbine erfordert einen sehr komplexen Regelkreis sowie Stellventile, die eine hinreichend schnelle Regelung gestatten. Bisher werden ausschließlich hydraulisch angetriebene Stellventeile zur Dampfeinlassregelung verwendet, da nur über einen solchen hydraulischen Antrieb eine hinreichend schnelle Einstellung des Ventilhubs möglich ist. A method for regulating a steam turbine emerges the article "Practical design of speed and power controllers for steam turbines "by Johannes Dastych and Heinz Unbehauen, Martin Bennauer and Heribert Werthes, ATP 41 (1999), No. 5. A steam turbine is based on speed or Performance regulated. The control loop for speed and power according to figure 2 consists of function blocks such as speed / Capacity controller (D- / LR), live steam control valve (FD-STV), Interception control valve (AF-STV), steam generator (DE) and turbine (T) as well as elementary blocks, e.g. Constant, ramp and Jump function for the input signals. For deployment electrical power, the turbo set is powered by steam from one Steam generator supplied, the steam supply via control valves is regulated so that the necessary performance is available stands. The speed and the power are regulated via a common speed / power controller both for load operation with selectable statics as well as for regulation the speed at idle. The output signal of the speed / power controller acts on the live steam and interception control valves. Such a regulation of a steam turbine requires a very complex control loop and control valves that allow a sufficiently quick regulation. So far only hydraulically driven control valves for Steam inlet control used because only such hydraulic drive a sufficiently quick setting valve lift is possible.

Ein Stellantrieb für ein Ventil einer Dampfturbine mit einem elektromotorischen Antrieb ist bekannt aus der WO98/13633. Ein solcher elektromotorischer Antrieb ist besonders kostengünstig und verringert zudem eine Brandgefahr durch Vermeidung des Einsatzes von Hydrauliköl. Ein solcher elektromotorischer Antrieb für ein Dampfventil kann für ein Schnellschlußventil einer Dampfturbine zum Einsatz kommen, bei dem es nur auf ein schnelles Schließen der Dampfleitung ankommt. Zur Dampfturbinenregelung sind die elektromotorischen Antriebe aber ungeeignet, da für die erforderlichen Ventilhubstellungen die Stellzeiten zu gering und die Ventilhubeinstellungen zu ungenau sind.An actuator for a valve of a steam turbine with one Electromotive drive is known from WO98 / 13633. Such an electric motor drive is particularly inexpensive and also reduces the risk of fire by avoiding it the use of hydraulic oil. Such an electromotive Drive for a steam valve can be used for a Quick-closing valve of a steam turbine are used, where it is only a quick closing of the steam line arrives. The electromotive are for steam turbine control However, drives are unsuitable because they are necessary Valve stroke positions, the positioning times too short and the valve stroke settings are too imprecise.

Aufgabe der Erfindung ist die Angabe eines Verfahrens zur Regelung einer Dampfturbine, das insbesondere sehr kostengünstig ist und zudem eine erhöhte Betriebssicherheit bietet. Weitere Aufgabe der Erfindung ist die Angabe einer Dampfturbine mit den gleichen Vorteilen.The object of the invention is to provide a control method a steam turbine, which is particularly very inexpensive and also offers increased operational reliability. Another object of the invention is to provide a steam turbine with the same advantages.

Erfindungsgemäß wird die auf ein Verfahren gerichtete Aufgabe gelöst durch die Angabe eines Verfahrens zur Regelung einer Dampfturbine, bei dem Dampf der Dampfturbine über mindestens drei Ventile zugeführt wird, wobei eines der Ventile als ein Regelventil geregelt und mindestens zwei Ventile als Steuerventile gesteuert werden.According to the invention, the object is directed to a method solved by specifying a procedure for regulating a Steam turbine, where the steam of the steam turbine over at least three valves is supplied, one of the valves as one Control valve regulated and at least two valves as control valves to be controlled.

Es wird somit der völlig neue Weg eingeschlagen, bei der Regelung einer Dampfturbine Ventile zweier verschiedener Kategorien zu verwenden. Die Erfindung geht dabei von der Erkenntnis aus, dass zur effizienten, sicheren und schnellen Regelung der Dampfturbine keineswegs alle Ventile als Regelventile ausgebildet sein müssen, so wie es die bisher übliche Auffassung war. Nach umfangreichen Tests konnte vielmehr belegt werden, dass eine Kombination aus Regelventilen und Steuerventilen tatsächlich eine ausreichend sichere und schnelle Regelung der Dampfturbine ermöglicht. Die Steuerventile werden dabei abhängig von einem Reglerausgangssignal auf einen bestimmten Wert ihres Ventilhubs eingestellt. Die Beibehaltung eines Regeldifferenzwertes von etwa Null wird von einem, gegebenenfalls auch mehreren, Regelventilen übernommen. Somit können mindestens zwei Regelventile durch sehr viel einfachere Steuerventile ersetzt werden, wodurch der Regelkreis erheblich vereinfacht wird.

  • A) Bevorzugt werden die Steuerventile elektromotorisch angetrieben. Ein elektromotorischer Antrieb bietet gegenüber einem etwa elektrohydraulischen Antrieb erhebliche Kostenvorteile. Darüber hinaus verringert sich das Brandrisiko durch den Wegfall von Hydrauliköl. Durch die Übernahme der Feinregelung mittels des Regelventils genügt auch die geringere Stelldynamik bei dem elektromotorischen Antrieb für den Einsatz im Regelprozess.
  • B) Bevorzugt werden zwei Regelventile und zwei Steuerventile verwendet. Üblicherweise kommen bei Regelprozessen in der Dampfturbine vier Ventile zum Einsatz. Grundsätzlich genügt nach dem neuen Regelkonzept ein Regelventil, das mit drei Steuerventilen zusammenarbeitet. Hinsichtlich einer verbesserten Verfügbarkeit ist es jedoch vorteilhaft, zwei Regelventile und zwei Steuerventile zu verwenden.
  • C) Vorzugsweise wird das Verfahren bei einer Leistungsaufnahme der Dampfturbine so gestaltet, dass zunächst das Regelventil öffnet und bei Überschreiten eines festgelegten ersten Wertes eines für die Regelung des Regelventils verwendeten Reglerausgangssignals und bei Vorliegen einer positiven Regeldifferenz eines der Steuerventile öffnet. Weiter bevorzugt liegt der erste Wert etwa bei einem Viertel des maximalen Reglerausgangssignals. Die positive Regeldifferenz zeigt an, dass der gewünschte Wert für die Leistung oder auch die Drehzahl noch nicht erreicht ist.
  • D) Weiter bevorzugt öffnet beim Überschreiten eines zweiten Wertes des Reglerausgangssignals und bei Vorliegen einer positiven Regeldifferenz das zweite Regelventil. Der zweite Wert des Reglerausgangssignals ist dabei größer als der erste Wert des Reglerausgangssignals. Es wird somit eine weitere Stufe bei der Leistungsaufnahme erreicht, bei der das dritte Ventil, und zwar das zweite Regelventil, zugeschaltet wird. Der zweite Wert des Reglerausgangssignals liegt dabei weiter bevorzugt bei etwa der Hälfte des maximalen Werts des Reglerausgangssignals.
  • E) Vorzugsweise öffnet bei Überschreiten eines dritten Wertes des Reglerausgangssignals und bei Vorliegen einer positiven Regeldifferenz das zweite Steuerventil. Der dritte Wert des Reglerausgangssignals liegt dabei über dem Wert des zweiten Wertes des Reglerausgangssignals. Es wird somit eine weitere Stufe bei der Leistungsaufnahme der Dampfturbine erreicht, bei der das zweite Steuerventil zugeschaltet wird. Bei einem Reglerausgangssignal von 100% sind alle Ventile vollständig geöffnet.
  • F) Vorzugsweise wird eine Schließgeschwindigkeit jedes der Steuerventile abhängig von der jeweils vorliegenden Größe der Regeldifferenz eingestellt. Die Regeldifferenz gibt, wie ausgeführt, den Unterschied zwischen dem Soll- und dem Istwert der Drehzahl oder der Leistung der Dampfturbine an. Bei einer großen Regeldifferenz werden die Steuerventile mit einer großen Geschwindigkeit in ihre Sollstellung gefahren. Bei einer kleineren Regeldifferenz genügt eine kleinere Stellgeschwindigkeit. Für die elektromotorischen Antriebe kann insbesondere ein Frequenzumrichter abhängig vom Vorzeichen der Regeldifferenz die Stellrichtung für die Regelventile vorgeben.
    • This is the completely new way of using valves from two different categories when regulating a steam turbine. The invention is based on the knowledge that in order to control the steam turbine efficiently, safely and quickly, it is by no means necessary for all of the valves to be designed as control valves, as was the conventional view up to now. After extensive tests, it was rather possible to prove that a combination of control valves and control valves actually enables the steam turbine to be controlled sufficiently and quickly. The control valves are set depending on a controller output signal to a certain value of their valve lift. The maintenance of a control difference value of approximately zero is carried out by one, possibly also several, control valves. This means that at least two control valves can be replaced by much simpler control valves, which considerably simplifies the control circuit.
  • A) The control valves are preferably driven by an electric motor. An electric motor drive offers considerable cost advantages over an electro-hydraulic drive, for example. In addition, the risk of fire is reduced by the absence of hydraulic oil. By adopting the fine control by means of the control valve, the lower dynamic range of the electromotive drive is also sufficient for use in the control process.
  • B) Two control valves and two control valves are preferably used. Four valves are usually used in control processes in the steam turbine. Basically, according to the new control concept, a control valve that works with three control valves is sufficient. With regard to improved availability, however, it is advantageous to use two control valves and two control valves.
  • C) Preferably, the method is designed with a power consumption of the steam turbine so that the control valve opens first and one of the control valves opens when a predetermined first value of a controller output signal used for the control of the control valve is exceeded and when a positive control difference is present. The first value is more preferably approximately a quarter of the maximum controller output signal. The positive control difference indicates that the desired value for the power or the speed has not yet been reached.
  • D) With further preference, the second control valve opens when a second value of the controller output signal is exceeded and when there is a positive control difference. The second value of the controller output signal is larger than the first value of the controller output signal. A further stage in power consumption is thus reached in which the third valve, namely the second control valve, is switched on. The second value of the controller output signal is more preferably approximately half the maximum value of the controller output signal.
  • E) Preferably, the second control valve opens when a third value of the controller output signal is exceeded and when there is a positive control difference. The third value of the controller output signal is above the value of the second value of the controller output signal. A further stage in the power consumption of the steam turbine is thus reached, in which the second control valve is activated. With a controller output signal of 100%, all valves are fully open.
  • F) A closing speed of each of the control valves is preferably set as a function of the respectively present size of the control difference. The control difference, as stated, indicates the difference between the setpoint and the actual value of the speed or the power of the steam turbine. If there is a large control difference, the control valves are moved into their target position at high speed. With a smaller control difference, a lower actuating speed is sufficient. For the electromotive drives, a frequency converter, in particular, can specify the setting direction for the control valves depending on the sign of the control difference.

    • Die Ausgestaltungen nach den Punkten A bis F können in beliebiger Weise miteinander kombiniert werden.The configurations according to points A to F can be in any Can be combined with each other.

    Die auf eine Dampfturbine gerichtete Aufgabe wird erfindungsgemäß gelöst durch Angabe einer Dampfturbine mit einer Ventilgruppe zur Regelung des Dampfeinlasses, welche Ventilgruppe ein Regelventil und mindestens zwei Steuerventile umfaßt.The object directed to a steam turbine is achieved according to the invention solved by specifying a steam turbine with a valve group to control the steam inlet, which valve group includes a control valve and at least two control valves.

    Die Vorteile einer solchen Dampfturbine ergeben sich entsprechend den obigen Ausführungen zu den Vorteilen des Verfahrens zur Regelung einer Dampfturbine .The advantages of such a steam turbine result accordingly the above comments on the advantages of the method to control a steam turbine.

    Vorzugsweise weisen die Steuerventile einen elektromotorischen Antrieb auf.The control valves preferably have an electromotive one Drive on.

    Die Erfindung wird anhand der Zeichnung beispielhaft näher erläutert. Es zeigen schematisch und nicht maßstäblich:

    FIG 1
    eine Dampfturbinenanlage,
    FIG 2
    einen Satz von Dampfeinlaßventilen mit zugehöriger Regelungsbeschaltung und
    FIG 3
    eine Kennliniendarstellung für die Dampfeinlaßventile.
    The invention is explained in more detail by way of example with reference to the drawing. They show schematically and not to scale:
    FIG. 1
    a steam turbine plant,
    FIG 2
    a set of steam inlet valves with associated control circuitry and
    FIG 3
    a representation of the characteristic curve for the steam inlet valves.

    Gleiche Bezugszeichen haben in den verschiedenen Figuren die gleiche Bedeutung.The same reference numerals have in the different figures same meaning.

    Figur 1 zeigt schematisch eine Dampfturbinenanlage. Einer Dampfturbine 1 wird Dampf aus einem Dampferzeuger 3 über die Zufuhrleitung 5 zugeführt. In die Zufuhrleitung 5 ist eine Ventilgruppe 7 eingebaut. Die Ventilgruppe 7 umfaßt ein erstes Regelventil 9 und ein zweites Regelventil 11. Die Ventilgruppe 7 umfaßt weiter ein erstes Steuerventil 13 und ein zweites Steuerventil 15. Über die Ventilgruppe 7 wird die in die Dampfturbine 1 eingeleitete Dampfmenge geregelt. Dies geschieht in Abhängigkeit von der für die Dampfturbine 1 gewünschte Leistung oder Drehzahl. Dies wird näher anhand der Figuren 2 und 3 erläutert. Figure 1 shows schematically a steam turbine system. one Steam turbine 1 is steam from a steam generator 3 via the Supply line 5 supplied. In the supply line 5 is one Valve group 7 installed. The valve group 7 comprises a first one Control valve 9 and a second control valve 11. The valve group 7 further includes a first control valve 13 and a second control valve 15. Via the valve group 7, the in the steam turbine 1 regulates the amount of steam introduced. this happens depending on the one desired for the steam turbine 1 Power or speed. This is explained in more detail using the Figures 2 and 3 explained.

    Figur 2 zeigt die Ventilgruppe 7 aus Figur 1 mit der zugehörigen Regelungsbeschaltung. Ein Regler 21 erzeugt abhängig vom Istwert der Drehzahl oder Leistung und dem Sollwert der Drehzahl oder Leistung ein Reglerausgangssignal kennzeichnend für eine Regeldifferenz. Das Reglerausgangssignal wird einem ersten Servöverstärker 23 des ersten Regelventils 9 zugeleitet. Das Reglerausgangssignal wird auch einem zweiten Servoverstärker 27 des zweiten Regelventils 11 zugeleitet. Das Reglerausgangssignal wird auch einem ersten Frequenzumrichter 25 des ersten Steuerventils 13 zugeleitet. Das Reglerausgangssignal wird auch einem zweiten Frequenzumrichter 29 des zweiten Steuerventils 15 zugeleitet. Das Regelungsverfahren wird näher anhand von Figur 3 beschrieben.FIG. 2 shows the valve group 7 from FIG. 1 with the associated one Regelungsbeschaltung. A controller 21 generates depending from the actual value of the speed or power and the setpoint of Speed or power characterizing a controller output signal for a control difference. The controller output signal is one first servo amplifier 23 of the first control valve 9 fed. The controller output signal also becomes a second servo amplifier 27 of the second control valve 11 fed. The Controller output signal is also a first frequency converter 25 of the first control valve 13 fed. The controller output signal is also a second frequency converter 29 of the second control valve 15 fed. The regulatory process is described in more detail with reference to Figure 3.

    Figur 3 zeigt in einem Diagramm beispielhaft den Ventilhub jedes der Ventile 9, 11, 13, 15 in Abhängigkeit vom Reglerausgangssignal. Die Angaben sind in Prozent vom jeweiligen Maximalwert dargestellt. Die Kennlinie 9K gibt den Verlauf des Ventilhubs 33 des ersten Reglerventils 9 in Abhängigkeit vom Reglerausgangssignal 31 an. Die Kennlinie 13K gibt die entsprechende Kennlinie für das erste Steuerventil 13 an. Die Kennlinie 11K gibt die entsprechende Kennlinie für das zweite Regelventil 11 an. Die Kennlinie 15K gibt die entsprechende Kennlinie für das zweite Steuerventil 15 an. Das erste Regelventil 9 öffnet proportional zur Größe des Reglerausgangssignals 31. Bei einem Wert von 22,5% des Reglerausgangssignals 31 öffnet das erste Steuerventil 13. Bei einem Wert von 47,5% des Reglerausgangssignals 31 ist der Ventilhub 33 für das erste Regelventil 9 und für das erste Steuerventil 13 bei 100%. Ab diesem Punkt öffnet sich das zweite Regelventil 11. Bei einem Wert von 72,5% wird schließlich das zweite Steuerventil 15 zugeschaltet. Bei einem Wert von 100% des Reglerausgangssignals 31 sind alle Ventile 9, 11, 13, 15 vollständig geöffnet. Das Anfahren, Hochfahren auf Nenndrehzahl und die Synchronisierung erfolgt mit dem ersten Regelventil 9. Die Größe der Regeldifferenz bestimmt die Öffnungsgeschwindigkeit der Steuerventile 13, 15. Bei Lastabwürfen kommt es zu einer negativen Regeldifferenz. Die Größe der Negativ-Regeldifferenz bestimmt die Schließgeschwindigkeit der Steuerventile. Aufgrund der geringeren Stelldynamik der Steuerventile, die im gezeigten Beispiel elektromotorisch angetrieben werden, kann der Ansprechwert für einen Schaltvorgang "Schließen" bei Lastabwurf für die Regelventile 9, 11 und die Steuerventile 13, 15 unterschiedlich sein.Figure 3 shows an example of the valve lift in a diagram each of the valves 9, 11, 13, 15 depending on the controller output signal. The information is in percent of the respective Maximum value shown. The characteristic curve 9K gives the course of the valve lift 33 of the first regulator valve 9 in dependence from the controller output signal 31. The characteristic curve 13K gives that corresponding characteristic for the first control valve 13. The Characteristic 11K gives the corresponding characteristic for the second Control valve 11 on. The characteristic 15K gives the corresponding one Characteristic curve for the second control valve 15. The first control valve 9 opens proportional to the size of the controller output signal 31. At a value of 22.5% of the controller output signal 31 opens the first control valve 13. At a value of 47.5% of the controller output signal 31 is the valve lift 33 for the first control valve 9 and for the first control valve 13 at 100%. From this point on, the second control valve 11 opens. At a value of 72.5%, the second control valve will eventually 15 switched on. At a value of 100% of the controller output signal 31, all valves 9, 11, 13, 15 are complete open. Starting, ramping up to nominal speed and synchronization takes place with the first control valve 9. The size of the control difference determines the opening speed of the control valves 13, 15. When there are load shedding to a negative control difference. The size of the negative control difference determines the closing speed of the control valves. Due to the lower control dynamics of the control valves, which are driven by an electric motor in the example shown the response value for a switching operation "Close" for load shedding for the control valves 9, 11 and Control valves 13, 15 may be different.

    Claims (9)

    Verfahren zur Regelung einer Dampfturbine (1),
    bei dem Dampf der Dampfturbine (1) über mindestens drei Ventile (9, 11, 13, 15) zugeführt wird, wobei eines der Ventile (9, 11) als ein Regelventil geregelt und mindestens zwei Ventile (13, 15) als Steuerventile gesteuert werden.    Process for controlling a steam turbine (1),
    the steam is fed to the steam turbine (1) via at least three valves (9, 11, 13, 15), one of the valves (9, 11) being regulated as a control valve and at least two valves (13, 15) being controlled as control valves ,         Verfahren nach Anspruch 1,
    bei dem die Steuerventile (13, 15) elektromotorisch angetrieben werden.    Method according to claim 1,
    in which the control valves (13, 15) are driven by an electric motor.         Verfahren nach Anspruch 1,
    bei dem zwei Regelventile (9, 11) und zwei Steuerventile (13, 15) verwendet werden.    Method according to claim 1,
    in which two control valves (9, 11) and two control valves (13, 15) are used.         Verfahren nach Anspruch 1,
    bei dem für eine Leistungsaufnahme der Dampfturbine (1) zunächst das Regelventil (9, 11) öffnet und bei Überschreiten eines festgelegten ersten Wertes eines für die Regelung des Regelventils (9,11) verwendeten Reglerausgangssignals (31) und bei Vorliegen einer positiven Regeldifferenz eines der Steuerventile (13,15) öffnet.    Method according to claim 1,
    in which the control valve (9, 11) first opens for a power consumption of the steam turbine (1) and, when a predetermined first value of a controller output signal (31) used for the control of the control valve (9, 11) is exceeded and when there is a positive control difference, one of the Control valves (13, 15) opens.         Verfahren nach Anspruch 4 und 3,
    bei dem bei Überschreiten eines zweiten Wertes des Reglerausgangssignals (31) und bei Vorliegen einer positiven Regeldifferenz das zweite Regelventil (11) öffnet.    Method according to claims 4 and 3,
    at which the second control valve (11) opens when a second value of the controller output signal (31) is exceeded and when there is a positive control difference.         Verfahren nach Anspruch 4 und 3,
    bei dem bei Überschreiten eines dritten Wertes des Reglerausgangssignals (31) und bei Vorliegen einer positiven Regeldifferenz das zweite Steuerventil (15) öffnet.    Method according to claims 4 and 3,
    where the second control valve (15) opens when a third value of the controller output signal (31) is exceeded and when there is a positive control difference.         Verfahren nach Anspruch 1,
    bei dem eine Schliessgeschwindigkeit jedes der Steuerventile (13, 15) abhängig von der jeweils vorliegenden Größe der Regeldifferenz eingestellt wird.    Method according to claim 1,
    at which a closing speed of each of the control valves (13, 15) is set as a function of the respective size of the control difference.         Dampfturbine (1) mit einer Ventilgruppe (7) zur Regelung des Dampfeinlasses, welche Ventilgruppe (7) ein Regelventil (9, 11) und mindestens zwei Steuerventile (13, 15) umfasst.Steam turbine (1) with a valve group (7) for regulation of the steam inlet, which valve group (7) is a control valve (9, 11) and at least two control valves (13, 15). Dampfturbine (1) nach Anspruch 8, bei der die Steuerventile (13, 15) einen elektromotorischen Antrieb aufweisen.Steam turbine (1) according to claim 8, wherein the control valves (13, 15) have an electric motor drive.
    EP00120574A 2000-09-20 2000-09-20 Method for regulating a steam turbine and steam turbine Withdrawn EP1191190A1 (en)

    Priority Applications (7)

    Application Number Priority Date Filing Date Title
    EP00120574A EP1191190A1 (en) 2000-09-20 2000-09-20 Method for regulating a steam turbine and steam turbine
    ES01983470T ES2344591T3 (en) 2000-09-20 2001-09-07 PROCEDURE FOR REGULATING A STEAM TURBINE AND STEAM TURBINE.
    CNB018159753A CN100335751C (en) 2000-09-20 2001-09-07 Method for regulating steam turbine and corresponding steam turbine
    DE50115502T DE50115502D1 (en) 2000-09-20 2001-09-07 METHOD FOR REGULATING A STEAM TURBINE AND STEAM TURBINE
    JP2002529646A JP4695822B2 (en) 2000-09-20 2001-09-07 Method for regulating a steam turbine and a steam turbine
    PCT/EP2001/010358 WO2002025067A1 (en) 2000-09-20 2001-09-07 Method for regulating a steam turbine, and corresponding steam turbine
    EP01983470A EP1319117B1 (en) 2000-09-20 2001-09-07 Method for regulating a steam turbine, and corresponding steam turbine

    Applications Claiming Priority (1)

    Application Number Priority Date Filing Date Title
    EP00120574A EP1191190A1 (en) 2000-09-20 2000-09-20 Method for regulating a steam turbine and steam turbine

    Publications (1)

    Publication Number Publication Date
    EP1191190A1 true EP1191190A1 (en) 2002-03-27

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    ID=8169887

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    EP00120574A Withdrawn EP1191190A1 (en) 2000-09-20 2000-09-20 Method for regulating a steam turbine and steam turbine
    EP01983470A Expired - Lifetime EP1319117B1 (en) 2000-09-20 2001-09-07 Method for regulating a steam turbine, and corresponding steam turbine

    Family Applications After (1)

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    EP01983470A Expired - Lifetime EP1319117B1 (en) 2000-09-20 2001-09-07 Method for regulating a steam turbine, and corresponding steam turbine

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    EP (2) EP1191190A1 (en)
    JP (1) JP4695822B2 (en)
    CN (1) CN100335751C (en)
    DE (1) DE50115502D1 (en)
    ES (1) ES2344591T3 (en)
    WO (1) WO2002025067A1 (en)

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    EP1528446A1 (en) * 2003-10-29 2005-05-04 Siemens Aktiengesellschaft Method and controller for positioning an actuator and use of the controller
    DE102005033292A1 (en) * 2005-07-16 2007-01-25 I.N.T.-Rickert Gmbh Adhesive/sealing material applying device for use at motor vehicle door, has control valve, having body actuated by servo converter, controlled by signals to adjust its discharge pressure to preset value, independent of input pressure
    WO2019217632A1 (en) 2018-05-09 2019-11-14 Abb Schweiz Ag Turbine control system

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    CN103244203B (en) * 2013-05-21 2014-12-03 国家电网公司 Throttle valve system and working method thereof
    CN108252752B (en) * 2017-12-22 2020-05-12 东方电气集团东方汽轮机有限公司 Steam turbine steam inlet adjusting method
    CN109356674A (en) * 2018-12-25 2019-02-19 大庆特博科技发展有限公司 A kind of organic working medium turbine of adjustable nozzle quantity

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    Also Published As

    Publication number Publication date
    JP2004518050A (en) 2004-06-17
    DE50115502D1 (en) 2010-07-15
    EP1319117B1 (en) 2010-06-02
    CN100335751C (en) 2007-09-05
    ES2344591T3 (en) 2010-09-01
    JP4695822B2 (en) 2011-06-08
    EP1319117A1 (en) 2003-06-18
    WO2002025067A1 (en) 2002-03-28
    CN1461374A (en) 2003-12-10

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