EP1319117B1 - Method for regulating a steam turbine, and corresponding steam turbine - Google Patents

Method for regulating a steam turbine, and corresponding steam turbine Download PDF

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Publication number
EP1319117B1
EP1319117B1 EP01983470A EP01983470A EP1319117B1 EP 1319117 B1 EP1319117 B1 EP 1319117B1 EP 01983470 A EP01983470 A EP 01983470A EP 01983470 A EP01983470 A EP 01983470A EP 1319117 B1 EP1319117 B1 EP 1319117B1
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EP
European Patent Office
Prior art keywords
control
steam turbine
valves
valve
steam
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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.)
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EP01983470A
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German (de)
French (fr)
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EP1319117A1 (en
Inventor
Heinrich Oeynhausen
Richard Steinborn
Heribert Werthes
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Siemens AG
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Siemens AG
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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, in which steam is supplied to the steam turbine via at least three valves.
  • the invention further relates to a steam turbine with a valve group for controlling the steam inlet.
  • a method for controlling a steam turbine is apparent from 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), Issue 5 , A steam turbine is regulated according to speed or power.
  • the control circuit for speed and power as shown in Figure 2 consists of function blocks such as speed / power controller (D- / LR), live steam control valve (FD-STV), intercept valve (AF-STV), steam generator (DE) and turbine (T) and elementary blocks, such as constant, ramp and step function for the input signals.
  • the turbo set is supplied with steam from a steam generator, wherein the steam supply via control valves is controlled so that the necessary power is available.
  • the output signal of the speed / power controller acts on the main steam and interception valves.
  • Such regulation of a steam turbine requires a very complex control circuit and control valves, which allow a sufficiently fast control. So far only hydraulically driven control valves are used for steam inlet control, since only a hydraulic drive such a sufficiently fast adjustment of the valve lift is possible.
  • An actuator for a valve of a steam turbine with an electric motor drive is known from the WO98 / 13633 , Such an electric motor drive is particularly inexpensive and also reduces a fire hazard by avoiding the use of hydraulic oil.
  • Such an electric motor drive for a steam valve can be used for a quick-closing valve of a steam turbine, in which it depends only on a quick closing of the steam line.
  • the electromotive drives are unsuitable because the required valve lift positions, the operating times are too low and the valve lift settings are too inaccurate.
  • a method for controlling a steam turbine according to the preamble of claim 1 is known from DE 272 691 C known.
  • the object of the invention is to specify a method for controlling a steam turbine, which is particularly cost-effective and also offers increased reliability.
  • Another object of the invention is the specification of a steam turbine with the same advantages.
  • the object directed to a method is achieved by specifying a method for controlling a steam turbine according to the features of claim 1.
  • the invention is based on the recognition that for efficient, safe and fast control of the steam turbine by no means all valves must be designed as control valves, as was the usual view. After extensive tests, it could be proven that a combination of control valves and control valves actually allows a sufficiently safe and fast control of the steam turbine.
  • the control valves are dependent on a controller output signal set a specific value of their valve lift. The maintenance of a control difference value of about zero is taken from one, possibly even more, control valves. Thus, at least two control valves can be replaced by much simpler control valves, whereby the control loop is considerably simplified.
  • the method is designed at a power consumption of the steam turbine so that first opens the control valve and opens when exceeding a predetermined first value of a controller output signal used for the control of the control valve and in the presence of a positive control difference of the control valves. More preferably, the first value is approximately one 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.
  • the task directed to a steam turbine is achieved according to the invention by specifying a steam turbine with a valve group for controlling the steam inlet according to claim 6.
  • control valves on an electric motor drive.
  • FIG. 1 schematically shows a steam turbine plant.
  • a steam turbine 1 is supplied with steam from a steam generator 3 via the supply line 5.
  • a valve group 7 is installed in the supply line 5.
  • the valve group 7 comprises a first control valve 9 and a second control valve 11.
  • the valve group 7 further comprises a first control valve 13 and a second control valve 15.
  • Via the valve group 7, the amount of steam introduced into the steam turbine 1 is regulated. This happens as a function of the desired power or speed for the steam turbine 1. This will be closer to the Figures 2 and 3 explained.
  • FIG. 2 shows the valve group 7 FIG. 1 with the associated control circuit.
  • a controller 21 generates depending on the actual value of the speed or power and the target value of the speed or power a controller output signal indicative of a control difference.
  • the regulator output signal is fed to a first servo amplifier 23 of the first control valve 9.
  • the regulator output signal is also supplied to a second servo amplifier 27 of the second control valve 11.
  • the regulator output signal is also supplied to a first frequency converter 25 of the first control valve 13.
  • the regulator output signal is also supplied to a second frequency converter 29 of the second control valve 15.
  • FIG. 3 shows in a diagram by way of example the valve lift of each of the valves 9, 11, 13, 15 in response to the controller output signal.
  • the figures are shown as a percentage of the respective maximum value.
  • the characteristic curve 9K indicates the profile of the valve lift 33 of the first regulator valve 9 as a function of the regulator output signal 31.
  • the characteristic curve 13K indicates the corresponding characteristic curve for the first control valve 13.
  • the characteristic curve 11K indicates the corresponding characteristic curve for the second control valve 11.
  • the characteristic curve 15K indicates the corresponding characteristic curve for the second control valve 15.
  • the first control valve 9 opens in proportion to the size of the regulator output signal 31. At a value of 22.5% of the regulator output signal 31 opens the first control valve 13.
  • the controller output signal 31 is the valve 33 for the first control valve 9 and for the first control valve 13 at 100%. From this point, the second control valve 11 opens. At a value of 72.5%, the second control valve 15 is finally switched on. At a value of 100% of the controller output signal 31, all valves 9, 11, 13, 15 are fully opened. The start-up, ramping up to rated speed and the 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. With load drops it comes to a negative control difference. The size of the negative control difference determines the closing speed of the control valves. Due to the lower dynamic range of the control valves, which are driven by an electric motor in the example shown, the response value for a switching operation "closing" during load shedding for the control valves 9, 11 and the control valves 13, 15 may be different.

Abstract

The invention relates to a method for regulating a steam turbine (1), according to which steam is fed to the steam turbine (1) via at least three valves, whereby one of the valves is regulated as a regulating valve (9, 11), and at least two valves are controlled as control valves (13, 15).

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, in which steam is supplied to the steam turbine via at least three valves. 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 controlling a steam turbine is apparent from 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), Issue 5 , A steam turbine is regulated according to speed or power. The control circuit for speed and power as shown in Figure 2 consists of function blocks such as speed / power controller (D- / LR), live steam control valve (FD-STV), intercept valve (AF-STV), steam generator (DE) and turbine (T) and elementary blocks, such as constant, ramp and step function for the input signals. To provide electrical power, the turbo set is supplied with steam from a steam generator, wherein the steam supply via control valves is controlled so that the necessary power is available. The control of the speed and the power via a common speed / power controller both for the load operation with selectable statics and for controlling the speed at idle. The output signal of the speed / power controller acts on the main steam and interception valves. Such regulation of a steam turbine requires a very complex control circuit and control valves, which allow a sufficiently fast control. So far only hydraulically driven control valves are used for steam inlet control, since only a hydraulic drive such a sufficiently fast adjustment of the 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 an electric motor drive is known from the WO98 / 13633 , Such an electric motor drive is particularly inexpensive and also reduces a fire hazard by avoiding the use of hydraulic oil. Such an electric motor drive for a steam valve can be used for a quick-closing valve of a steam turbine, in which it depends only on a quick closing of the steam line. For steam turbine control, the electromotive drives are unsuitable because the required valve lift positions, the operating times are too low and the valve lift settings are too inaccurate.

Ein Verfahren zur Regelung einer Dampfturbine gemäß dem Oberbegriff des Anspruchs 1 ist aus der DE 272 691 C bekannt.A method for controlling a steam turbine according to the preamble of claim 1 is known from DE 272 691 C known.

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 specify a method for controlling a steam turbine, which is particularly cost-effective and also offers increased reliability. Another object of the invention is the specification of 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 gemäß den Merkmalen des Anspruch 1.According to the invention, the object directed to a method is achieved by specifying a method for controlling a steam turbine according to the features of claim 1.

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.It is thus taken the completely new way to use in controlling a steam turbine valves of two different categories. The invention is based on the recognition that for efficient, safe and fast control of the steam turbine by no means all valves must be designed as control valves, as was the usual view. After extensive tests, it could be proven that a combination of control valves and control valves actually allows a sufficiently safe and fast control of the steam turbine. The control valves are dependent on a controller output signal set a specific value of their valve lift. The maintenance of a control difference value of about zero is taken from one, possibly even more, control valves. Thus, at least two control valves can be replaced by much simpler control valves, whereby the control loop is considerably simplified.

Das Verfahren wird 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.The method is designed at a power consumption of the steam turbine so that first opens the control valve and opens when exceeding a predetermined first value of a controller output signal used for the control of the control valve and in the presence of a positive control difference of the control valves. More preferably, the first value is approximately one 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.

Die Steuerventile werden 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.

  1. A) 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.
  2. B) 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.
  3. C) 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.
  4. D) 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.
The control valves are driven by an electric motor. An electric motor drive offers considerable cost advantages over an approximately electro-hydraulic drive. In addition, the risk of fire is reduced by the elimination of hydraulic oil. By adopting the fine control by means of the control valve also satisfies the lower dynamic range in the electric motor drive for use in the control process.
  1. A) Preferably two control valves and two control valves are used. Normally, four valves are 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. However, in view of improved availability, it is advantageous to use two control valves and two control valves.
  2. B) Further preferably opens when exceeding a second value of the controller output signal and in the presence of a positive Control difference, the second control valve. The second value of the controller output signal is greater than the first value of the controller output signal. It is thus achieved a further stage in the power consumption, 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.
  3. C) Preferably, when a third value of the controller output signal is exceeded and in the presence of a positive control difference, the second control valve opens. The third value of the controller output signal is above the value of the second value of the controller output signal. It is thus achieved a further stage in the power consumption of the steam turbine, in which the second control valve is switched on. With a regulator output of 100%, all valves are fully open.
  4. D) Preferably, a closing speed of each of the control valves is set depending on the respective size of the control difference. The control difference indicates, as stated, the difference between the setpoint and the actual value of the speed or the power of the steam turbine. With a large control difference, the control valves are driven at a high speed to their desired position. With a smaller control difference, a smaller actuating speed is sufficient. For the electric motor drives, in particular a frequency converter depending on the sign of the control difference can specify the direction of adjustment for the control valves.

Die Ausgestaltungen nach den Punkten A bis D können in beliebiger Weise miteinander kombiniert werden.The embodiments according to the points A to D can be combined in any way with each other.

Die auf eine Dampfturbine gerichtete Aufgabe wird erfindungsgemäß gelöst durch Angabe einer Dampfturbine mit einer Ventilgruppe zur Regelung des Dampfeinlasses gemäß Anspruch 6.The task directed to a steam turbine is achieved according to the invention by specifying a steam turbine with a valve group for controlling the steam inlet according to claim 6.

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 arise in accordance with the above statements on the advantages of the method for controlling a steam turbine.

Vorzugsweise weisen die Steuerventile einen elektromotorischen Antrieb auf.Preferably, the control valves on an electric motor drive.

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 Dampfeinlaßven- tile.
The invention will be explained in more detail by way of example with reference to the drawing. Shown schematically and not to scale:
FIG. 1
a steam turbine plant,
FIG. 2
a set of steam inlet valves with associated control circuit and
FIG. 3
a characteristic curve for the steam inlet valves.

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

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. FIG. 1 schematically shows a steam turbine plant. A steam turbine 1 is supplied with steam from a steam generator 3 via the supply line 5. In the supply line 5, a valve group 7 is installed. The valve group 7 comprises a first control valve 9 and a second control valve 11. The valve group 7 further comprises a first control valve 13 and a second control valve 15. Via the valve group 7, the amount of steam introduced into the steam turbine 1 is regulated. This happens as a function of the desired power or speed for the steam turbine 1. This will be closer to 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 Servoverstärker 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 FIG. 1 with the associated control circuit. A controller 21 generates depending on the actual value of the speed or power and the target value of the speed or power a controller output signal indicative of a control difference. The regulator output signal is fed to a first servo amplifier 23 of the first control valve 9. The regulator output signal is also supplied to a second servo amplifier 27 of the second control valve 11. The regulator output signal is also supplied to a first frequency converter 25 of the first control valve 13. The regulator output signal is also supplied to a second frequency converter 29 of the second control valve 15. The regulatory procedure will be described in more detail on the basis of FIG. 3 described.

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. FIG. 3 shows in a diagram by way of example the valve lift of each of the valves 9, 11, 13, 15 in response to the controller output signal. The figures are shown as a percentage of the respective maximum value. The characteristic curve 9K indicates the profile of the valve lift 33 of the first regulator valve 9 as a function of the regulator output signal 31. The characteristic curve 13K indicates the corresponding characteristic curve for the first control valve 13. The characteristic curve 11K indicates the corresponding characteristic curve for the second control valve 11. The characteristic curve 15K indicates the corresponding characteristic curve for the second control valve 15. The first control valve 9 opens in proportion to the size of the regulator output signal 31. At a value of 22.5% of the regulator output signal 31 opens the first control valve 13. At a value of 47.5% of the controller output signal 31 is the valve 33 for the first control valve 9 and for the first control valve 13 at 100%. From this point, the second control valve 11 opens. At a value of 72.5%, the second control valve 15 is finally switched on. At a value of 100% of the controller output signal 31, all valves 9, 11, 13, 15 are fully opened. The start-up, ramping up to rated speed and the 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. With load drops it comes to a negative control difference. The size of the negative control difference determines the closing speed of the control valves. Due to the lower dynamic range of the control valves, which are driven by an electric motor in the example shown, the response value for a switching operation "closing" during load shedding for the control valves 9, 11 and the control valves 13, 15 may be different.

Claims (7)

  1. Method for controlling a steam turbine (1),
    in which steam is supplied to the steam turbine (1) via at least three valves (9, 11, 13, 15), with one of the valves (9, 11) being regulated as a regulating valve and at least two valves (13, 15) being controlled as control valves, and with the regulating valve (9, 11) opening first of all for power consumption by the steam turbine (1), characterized in that with one of the control valves (13, 15) opening when a fixed first value for a regulator output signal (31), which is used for regulating the regulating valve (9, 11), is exceeded and a positive control difference is present, with the control valves (13, 15) being driven by electric motors.
  2. Method according to Claim 1,
    in which two regulating valves (9, 11) and two control valves (13, 15) are used.
  3. Method according to Claims 1 and 2,
    in which the second regulating valve (11) opens when the regulator output signal (31) exceeds a second value and a positive control difference is present.
  4. Method according to Claims 1 and 2,
    in which the second control valve (15) opens when the regulator output signal (31) exceeds a third value and a positive control difference is present.
  5. Method according to Claim 1,
    in which a closing rate for each of the control valves (13, 15) is set as a function of the respective magnitude of the control difference.
  6. Steam turbine (1) having a valve group (7) for controlling the steam inlet, which valve group (7) has a regulating valve (9, 11) and at least two control valves (13, 15),
    wherein the valve group (7) is designed with a regulator (21), wherein the regulator (21) is designed to control the steam inlet in accordance with a method according to one of Claims 1 to 5.
  7. Steam turbine (1) according to Claim 6, in which the control valves (13, 15) have an electric motor drive.
EP01983470A 2000-09-20 2001-09-07 Method for regulating a steam turbine, and corresponding steam turbine Expired - Lifetime EP1319117B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP01983470A EP1319117B1 (en) 2000-09-20 2001-09-07 Method for regulating a steam turbine, and corresponding steam turbine

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP00120574 2000-09-20
EP00120574A EP1191190A1 (en) 2000-09-20 2000-09-20 Method for regulating a steam turbine and 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

Publications (2)

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EP1319117A1 EP1319117A1 (en) 2003-06-18
EP1319117B1 true EP1319117B1 (en) 2010-06-02

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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

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JP (1) JP4695822B2 (en)
CN (1) CN100335751C (en)
DE (1) DE50115502D1 (en)
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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
DE102005033292B4 (en) * 2005-07-16 2007-07-26 I.N.T.-Rickert GmbH Ingenieurbüro für neue Technologien Device for applying adhesives or sealants
JP2013079580A (en) * 2011-09-30 2013-05-02 Toshiba Corp Method of operating combined power generating facility and combined power generating facility
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
JP2021523664A (en) * 2018-05-09 2021-09-02 アーベーベー・シュバイツ・アーゲーＡＢＢ Ｓｃｈｗｅｉｚ ＡＧ Circuit breaker automatic synchronization device
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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Publication number Priority date Publication date Assignee Title
DE272691C (en) *
NL26523C (en) * 1926-08-28 1900-01-01
NL29786C (en) * 1929-12-30 1932-12-15
FR787271A (en) * 1934-06-21 1935-09-19 Rateau Sa Steam or gas turbine adjustment device
US3763894A (en) * 1971-06-16 1973-10-09 Westinghouse Electric Corp Sequentially operable control valve for a steam turbine
US4245162A (en) * 1973-08-15 1981-01-13 Westinghouse Electric Corp. Steam turbine power plant having improved testing method and system for turbine inlet valves associated with downstream inlet valves preferably having feedforward position managed control
AU537607B2 (en) * 1980-12-02 1984-07-05 Hitachi Limited Combined valve for use in a reheating steam turbine
JPS57188705A (en) * 1981-05-15 1982-11-19 Toshiba Corp Steam turbine
US4604028A (en) * 1985-05-08 1986-08-05 General Electric Company Independently actuated control valves for steam turbine
JPH0261101U (en) * 1988-10-26 1990-05-07
DE19616178C2 (en) * 1995-07-14 1998-07-16 Ver Energiewerke Ag Method for loading and unloading the high pressure part of a steam turbine operated with a duo steam boiler block
DE59709519D1 (en) * 1996-09-26 2003-04-17 Siemens Ag VALVE OF A TURBINE

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DE50115502D1 (en) 2010-07-15
CN1461374A (en) 2003-12-10
ES2344591T3 (en) 2010-09-01
WO2002025067A1 (en) 2002-03-28
EP1191190A1 (en) 2002-03-27
EP1319117A1 (en) 2003-06-18
CN100335751C (en) 2007-09-05
JP4695822B2 (en) 2011-06-08
JP2004518050A (en) 2004-06-17

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