EP2037086B1 - Start-up of a steam turbine - Google Patents

Start-up of a steam turbine Download PDF

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Publication number
EP2037086B1
EP2037086B1 EP07014816.8A EP07014816A EP2037086B1 EP 2037086 B1 EP2037086 B1 EP 2037086B1 EP 07014816 A EP07014816 A EP 07014816A EP 2037086 B1 EP2037086 B1 EP 2037086B1
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Prior art keywords
valve
steam turbine
open position
steam
rotation
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EP07014816.8A
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German (de)
French (fr)
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EP2037086A1 (en
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Rudolf Dr. Keiper
Thomas Dr. Müller
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Siemens AG
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Siemens AG
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Priority to EP07014816.8A priority Critical patent/EP2037086B1/en
Priority to PL07014816T priority patent/PL2037086T3/en
Priority to PCT/EP2008/059241 priority patent/WO2009016029A2/en
Publication of EP2037086A1 publication Critical patent/EP2037086A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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
    • F01D19/00—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith

Definitions

  • the invention relates to a method for starting a steam turbine at a synchronous speed, which is operated in a cogeneration system with a boiler and at least one arranged between the boiler and the steam turbine in a steam line valve with a controllable open position, wherein a live steam pressure upstream of the valve is measured.
  • the invention relates to a control unit of a cogeneration system, which cogeneration system comprises a boiler and at least one to be operated at a synchronous speed steam turbine, wherein between the steam turbine and the boiler at least one arranged in a steam line valve with adjustable open position is provided, wherein a live steam pressure upstream of the valve is measured.
  • different dynamic behavior of individual components such as the boiler and the steam turbine can lead to unexpected operating conditions.
  • the boiler in which the steam generation and overheating takes place, essentially follows thermal time constants
  • the steam turbine in which the generated and superheated steam is expanded, follows with their speed behavior much shorter time constants than the boiler.
  • a so-called quick-acting valve which in certain as Fault classified events the steam supply from the boiler to the steam turbine interrupts.
  • the steam generated in the boiler is fed in bypass to the steam turbine to a reducing station, which either relaxes the circulating medium into the environment or, after expansion, introduces a condenser integrated in the circuit.
  • US 4,258,424 discloses a computer controlled control system for determining steam flow characteristics of a steam turbine.
  • the control valves are fully opened to introduce steam from a boiler into a turbine.
  • the control valves may be individually controlled to provide thermal equilibrium on the rotor and reduce rotor blade stress.
  • the steam turbine may be controlled based on steam control, speed control, or load control to meet predetermined safety limits and protection limits.
  • GB 2 084 260 A discloses a steam turbine control for a steam turbine in a steam turbine power plant.
  • the steam turbine power plant has a high-pressure turbine and a low-pressure turbine.
  • a main control valve, a high pressure bypass valve, a control valve and a low pressure bypass valve control the respective turbines.
  • the control valves are controlled based on the speed and temperature of the turbine.
  • the invention has therefore set itself the task of preventing unwanted fast-closing events at a power cogeneration system mentioned above.
  • the valve with adjustable opening position according to the invention is usually a so-called control valve, which is often used in combination with a so-called quick-closing valve.
  • the running between the boiler and the steam turbine steam line is usually a so-called live steam line.
  • the invention finds particularly advantageous use in a boiler which is fired with solids, in particular by means of combustible organic material, since such systems have a particularly different dynamic behavior compared to that of the steam turbine. In principle, however, the method or regulation according to the invention can be used for all cycles of the type mentioned above. While quick-acting valves usually only allow the fully open or completely closed position and are optimized for a particularly fast closing process, control valves allow a continuously variable adjustment of the opening between 0% and 100%.
  • the method according to the invention has the significant advantage that conventionally necessary and very complex coordination work between the control behavior of the steam turbine and that of the boiler can be reduced to a minimum or eliminated altogether.
  • the controller of the valve position essentially takes over the pressure control of the boiler or supports this, so that an occurrence of a quick-closing criterion from a critical pressure behavior of the boiler out is highly unlikely.
  • this phase occurs simultaneously due to the opening of the valve or control valve an increase in the speed of the steam turbine.
  • the specification of the setpoint for the open position of the valve is no longer dependent on the live steam pressure, but on the speed of the steam turbine, which is regularly specified as the control criterion for the speed of the setpoint synchronous speed.
  • the time of the changeover of the control for the opening position of the valve or the speed difference to the synchronous speed can be determined depending on the system conditions, the difference is rather low, when the boiler is very sensitive to the opening of the control valve with pressure drop.
  • the method according to the invention is used when using particularly tolerant turbo sets, which do not require any special speed transients, especially in resonance ranges for damage-free starting.
  • the predetermined difference value to the synchronous speed in which the control of the valve position is switched by the dependence on the live steam pressure depending on the speed, may suitably be between 1% and 10% of the synchronous speed, so that at a synchronous speed of 3000 rev / min after reaching A speed of about 2900 rev / min is switched to a speed control.
  • the control criterion during the start-up phase in which the valve position is controlled by the live steam pressure is preferably a constant live steam pressure of, for example, 2.5 bar.
  • FIG. 1 shows a schematic overview of a cogeneration system 1 with a control according to the invention using the start-up method according to the invention.
  • the combined heat and power system 1 consists essentially of a boiler B, a steam turbine ST, a generator G, a condenser Cond and a feedwater pump PU.
  • the boiler B the water delivered by the feed water pump PU to a pressure of about 3.5 bar is heated, evaporated and superheated by means of a heat supply QF.
  • the superheated live steam passes through a main steam line FSL passing a quick-closing valve ESV and a control valve CV to relax in the steam turbine ST, where under production of technical work, the live steam is expanded to condenser pressure which technical work drives a generator G, the electric power P in a Network GR feeds.
  • the turbo set consisting of steam turbine ST and generator G rotates at a synchronous speed n sync of 3000 U / min.
  • the condenser Cond the relaxed steam is condensed with the removal of heat QC.
  • the condensed water is pumped by the pump PU receiving the technical work WT to the boiler pressure of 3.5 bar.
  • the fuel supply QF to the boiler B is controlled by means of a boiler controller PID, which regulates the supply of solid fuel in response to the live steam pressure PF with the aim of keeping the live steam pressure constant at 3.5 bar.
  • the live steam pressure PF in the Main steam line FSL is measured by means of a pressure sensor PS.
  • the position of the control valve CV is controlled by means of a regulator PI.
  • a speed sensor NS By means of a speed sensor NS, the speed n of the turbo set of steam turbine ST and generator G is measured.
  • the speed n and the live steam pressure PF are input to a control unit CM, which controls or controls, among other things, the opening position of the control valve CV and the fuel supply QF via the controller PI or PID.
  • the quick-closing valve ESV In a first phase of the startup of the combined heat and power system 1, the quick-closing valve ESV is closed and the boiler B generates live steam under fuel supply QF, which is fed under passage through a bypass valve VR via a reducing station directly into the condenser Cond. Upon reaching unspecified criteria, such as steam purity or stability over a period of time, closes the bypass valve VR.
  • the quick-closing valve ESV opens simultaneously with the closing of the bypass valve VR and the control valve CV opens so far that about 50% of the maximum open position of the control valve CV are reached.
  • the live steam pressure PF drops slightly and the speed n of the steam turbine ST increases.
  • the control unit CM regulates the live steam pressure to 3.5 bar by means of suitable control of the control valve CV and the speed n of the steam turbine ST increases as a result.
  • control valve initially simply remains in the first open position of about 50% without further control of the live steam pressure and also not guided by the turbine speed n.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)

Description

Die Erfindung betrifft eine Methode zum Anfahren einer Dampfturbine auf eine Synchrondrehzahl, welche in einem Kraftwärmekopplungssystem mit einem Kessel und mindestens einer zwischen dem Kessel und der Dampfturbine in einer Dampfleitung angeordneten Ventil mit regelbarer Öffnungsstellung betrieben wird, wobei ein Frischdampfdruck stromaufwärts des Ventils gemessen wird. Daneben betrifft die Erfindung eine Regeleinheit eines Kraftwärmekopplungssystems, welches Kraftwärmekopplungssystem einen Kessel und mindestens eine bei einer Synchrondrehzahl zu betreibende Dampfturbine aufweist, wobei zwischen der Dampfturbine und dem Kessel mindestens ein in einer Dampfleitung angeordnetes Ventil mit regelbarer Öffnungsstellung vorgesehen ist, wobei ein Frischdampfdruck stromaufwärts des Ventils gemessen wird.The invention relates to a method for starting a steam turbine at a synchronous speed, which is operated in a cogeneration system with a boiler and at least one arranged between the boiler and the steam turbine in a steam line valve with a controllable open position, wherein a live steam pressure upstream of the valve is measured. In addition, the invention relates to a control unit of a cogeneration system, which cogeneration system comprises a boiler and at least one to be operated at a synchronous speed steam turbine, wherein between the steam turbine and the boiler at least one arranged in a steam line valve with adjustable open position is provided, wherein a live steam pressure upstream of the valve is measured.

Ein großer Anteil der Energieerzeugung erfolgt in einem Kraftwärmekopplungssystem der vorgenannten Art mittels einer oder mehrerer Dampfturbinen. Insbesondere während nicht stationärer Betriebsphasen dieser Systeme kann sich unterschiedliches dynamisches Verhalten einzelner Komponenten, beispielsweise des Kessels und der Dampfturbine zu unerwarteten Betriebszuständen führen. Hierbei verdient die Tatsache Beachtung, dass einerseits der Kessel, in welchem die Dampferzeugung und Überhitzung erfolgt, im Wesentlichen thermischen Zeitkonstanten folgt und andererseits die Dampfturbine, in welcher der erzeugte und überhitze Dampf entspannt wird, mit ihren Drehzahlverhalten viel kürzeren Zeitkonstanten als der Kessel folgt. Aus Gründen der Netzstabilität und sonstiger Sicherheitserwägungen befindet sich regelmäßig zwischen dem Kessel und der Dampfturbine neben dem Stellventil ein so genanntes Schnellschlussventil, das bei bestimmten als Störung klassifizierten Ereignissen die Dampfzufuhr aus dem Kessel zu der Dampfturbine unterbricht. In derartigen Fällen wird der im Kessel erzeugte Dampf im Bypass zu der Dampfturbine einer Reduzierstation zugeführt, die entweder das Kreislaufmedium in die Umgebung entspannt oder nach einer Entspannung einen in den Kreislauf integrierten Kondensator einleitet.A large proportion of energy production takes place in a cogeneration system of the aforementioned type by means of one or more steam turbines. In particular, during non-stationary operating phases of these systems, different dynamic behavior of individual components, such as the boiler and the steam turbine can lead to unexpected operating conditions. The fact that on the one hand the boiler, in which the steam generation and overheating takes place, essentially follows thermal time constants and on the other hand the steam turbine, in which the generated and superheated steam is expanded, follows with their speed behavior much shorter time constants than the boiler. For reasons of grid stability and other safety considerations is regularly located between the boiler and the steam turbine next to the control valve, a so-called quick-acting valve, which in certain as Fault classified events the steam supply from the boiler to the steam turbine interrupts. In such cases, the steam generated in the boiler is fed in bypass to the steam turbine to a reducing station, which either relaxes the circulating medium into the environment or, after expansion, introduces a condenser integrated in the circuit.

Das unterschiedliche dynamische Verhalten von Kessel und Dampfturbine kann insbesondere bei Feststoff-befeuerten Kesseln, deren Zeitkonstante in Folge der speziellen Eigenschaften der Befeuerung besonders groß ist, zu unerwünschten Schnellschlussereignissen führen. Hierbei sind mittels organischen Materials befeuerte Kessel besonders kritisch, weil die benutzten Brennstoffe in ihrem Brennverhalten schwierig zu beeinflussen sind. Beim Anfahren derartiger Systeme ereignet sich daher häufig ein Schnellschluss, wenn sich in dem Kessel der erforderliche Frischdampfdruck aufgebaut hat und das in der Frischdampfleitung befindliche Ventil zur Dampfturbine öffnet. Herkömmliche Ventilsteuerungen regeln die Öffnungsposition des Stellventils ausschließlich in Abhängigkeit von der Turbinendrehzahl, die nach einer bestimmten zeitlichen Kennlinie auf eine Synchrondrehzahl angefahren wird. Dieses Anfahren führt regelmäßig zu einem Absinken des Kesseldrucks bzw. des Drucks in der Frischdampfleitung, welcher den Regler des Kessels dazu veranlasst, die Brennstoffzufuhr zu erhöhen. In Ermangelung einer aufwändigen Abstimmung der einzelnen Reglerverhalten aufeinander führt dies regelmäßig dazu, dass die Brennstoffzufuhr des Kessels zu stark erhöht wird und der Kessel einen zu hohen Frischdampfdruck erzeugt, durch welchen die Energiezufuhr zur Dampfturbine zu groß werden kann und dementsprechend zu einem Schnellschluss führt, so dass der Dampf wie zuvor beschrieben über die Reduzierstation ohne technische Arbeit zu leisten entspannt wird. Derartige Schnellschlussereignisse sind naturgemäß unerwünscht, da sie einerseits Zeit kosten und andererseits Energie vernichten.The different dynamic behavior of boiler and steam turbine can lead to undesirable rapid-fire events, especially in solid-fired boilers, whose time constant is particularly high due to the special characteristics of the firing. Here are using organic material fired boilers are particularly critical because the fuels used are difficult to influence in their burning behavior. When starting up such systems, therefore, a quick closure often occurs when the required live steam pressure has built up in the boiler and the valve located in the main steam line opens to the steam turbine. Conventional valve controls regulate the opening position of the control valve exclusively in dependence on the turbine speed, which is approached after a certain time characteristic to a synchronous speed. This startup regularly leads to a decrease in the boiler pressure or the pressure in the main steam line, which causes the controller of the boiler to increase the fuel supply. In the absence of an elaborate coordination of the individual controller behavior to each other, this regularly leads to the fact that the fuel supply of the boiler is increased too much and the boiler generates too high live steam pressure through which the power supply to the steam turbine can be too large and accordingly leads to a quick closing, so that the steam is relaxed as described above via the reducing station without technical work. Such fast-closing events are naturally undesirable because they cost time and on the other hand destroy energy.

US 4,258,424 offenbart ein computergesteuertes Steuersystem zur Bestimmung von Dampfströmungseigenschaften einer Dampfturbine. Während eines Anfahrvorgangs einer Dampfturbine werden die Steuerventile vollständig geöffnet, um Dampf von einem Kessel in eine Turbine einzuleiten. Die Steuerventile können einzeln angesteuert werden, um ein thermisches Gleichgewicht auf dem Rotor bereitzustellen und eine Rotorblattbeanspruchung zu reduzieren. Während des Betriebs der Dampfturbine kann die Dampfturbine basierend auf einer Dampfsteuerung, einer Geschwindigkeitssteuerung oder abhängig von einer Belastungssteuerung gesteuert werden, um vorbestimmte Sicherheitsvorgaben und Schutzgrenzen einzuhalten. US 4,258,424 discloses a computer controlled control system for determining steam flow characteristics of a steam turbine. During startup of a steam turbine, the control valves are fully opened to introduce steam from a boiler into a turbine. The control valves may be individually controlled to provide thermal equilibrium on the rotor and reduce rotor blade stress. During operation of the steam turbine, the steam turbine may be controlled based on steam control, speed control, or load control to meet predetermined safety limits and protection limits.

GB 2 084 260 A offenbart eine Dampfturbinensteuerung für eine Dampfturbine in einem Dampfturbinenkraftwerk. Das Dampfturbinenkraftwerk weist eine Hochdruckturbine und eine Niederdruckturbine auf. Ein Hauptsteuerventil, ein Hochdruckbypassventil, ein Steuerventil und ein Niederdruckbypassventil steuern dabei die jeweiligen Turbinen. Die Steuerventile werden basierend auf der Drehzahl und der Temperatur der Turbine gesteuert. GB 2 084 260 A discloses a steam turbine control for a steam turbine in a steam turbine power plant. The steam turbine power plant has a high-pressure turbine and a low-pressure turbine. A main control valve, a high pressure bypass valve, a control valve and a low pressure bypass valve control the respective turbines. The control valves are controlled based on the speed and temperature of the turbine.

Die Erfindung hat es sich daher zur Aufgabe gemacht, unerwünschte Schnellschlussereignisse an einem eingangs genannten Kraftwärmekopplungssystem zu verhindern.The invention has therefore set itself the task of preventing unwanted fast-closing events at a power cogeneration system mentioned above.

Die gestellte Aufgabe wird durch eine Methode der eingangs genannten Art gelöst, bei welcher die im kennzeichnenden Teil des Anspruchs 1 beschriebenen Verfahrensschritte durchgeführt werden. Daneben schlägt die Erfindung zur Lösung des Problems eine Regelungseinheit nach dem Anspruch 7 vor. Die jeweils rückbezogenen Unteransprüche beinhalten vorteilhafte Weiterbildungen der Erfindung.The stated object is achieved by a method of the type mentioned, in which the method steps described in the characterizing part of claim 1 are performed. In addition, the invention proposes to solve the problem, a control unit according to claim 7. The respective dependent claims contain advantageous developments of the invention.

Bei dem Ventil mit regelbarer Öffnungsstellung nach der Erfindung handelt es sich in der Regel um ein sogenanntes Stellventil, das auch häufig in Kombination mit einem sogenannten Schnellschlussventil eingesetzt wird. Bei der zwischen dem Kessel und der Dampfturbine verlaufenden Dampfleitung handelt es sich in der Regel um eine sogenannte Frischdampfleitung. Besonders vorteilhaft findet die Erfindung Einsatz bei einem Kessel, der mit Feststoffen befeuert wird, insbesondere mittels brennbaren organischen Materials, da derartige Systeme ein besonders unterschiedliches dynamisches Verhalten im Vergleich zu demjenigen der Dampfturbine aufweisen. Grundsätzlich ist die erfindungsgemäße Methode bzw. Regelung jedoch für alle Kreisprozesse der eingangs genannten Art einsetzbar. Während Schnellschlussventile meist nur die ganz geöffnete oder ganz geschlossene Stellung ermöglichen und auf einen besonders schnellen Schließprozess optimiert sind, ermöglichen Stellventile eine regelmäßig stufenlose Verstellung der Öffnung zwischen 0% und 100%.The valve with adjustable opening position according to the invention is usually a so-called control valve, which is often used in combination with a so-called quick-closing valve. The running between the boiler and the steam turbine steam line is usually a so-called live steam line. The invention finds particularly advantageous use in a boiler which is fired with solids, in particular by means of combustible organic material, since such systems have a particularly different dynamic behavior compared to that of the steam turbine. In principle, however, the method or regulation according to the invention can be used for all cycles of the type mentioned above. While quick-acting valves usually only allow the fully open or completely closed position and are optimized for a particularly fast closing process, control valves allow a continuously variable adjustment of the opening between 0% and 100%.

Das erfindungsgemäße Verfahren hat den bedeutenden Vorteil, dass herkömmlich notwendige und sehr aufwändige Abstimmungsarbeiten zwischen dem Regelverhalten der Dampfturbine und demjenigen des Kessels auf ein Minimum reduziert werden oder ganz wegfallen können. Während des Anfahrvorganges der Dampfturbine übernimmt der Regler der Ventilstellung im Wesentlichen die Druckregelung des Kessels bzw. unterstützt diese, so dass ein Eintreten eines Schnellschlusskriteriums aus einem kritischen Druckverhalten des Kessels heraus höchst unwahrscheinlich wird. Während dieser Phase tritt gleichzeitig in Folge der Öffnung des Ventils bzw. Stellventils einer Erhöhung der Drehzahl der Dampfturbine ein. Kurz vor Erreichen der Synchrondrehzahl wird die Vorgabe des Sollwertes für die Öffnungsstellung des Ventils nicht mehr von dem Frischdampfdruck, sondern von der Drehzahl der Dampfturbine abhängig gemacht, wobei regelmäßig als Regelungskriterium für die Drehzahl der Sollwert der Synchrondrehzahl vorgegeben ist. Der Zeitpunkt der Umstellung der Regelung für die Öffnungsstellung des Ventils bzw. die Drehzahldifferenz zur Synchrondrehzahl kann hierbei in Abhängigkeit von den Systemgegebenheiten bestimmt werden, wobei die Differenz eher niedrig gewählt wird, wenn der Kessel sehr empfindlich auf das Öffnung des Stellventils mit Druckabfall reagiert. Vorzugsweise kommt die erfindungsgemäße Methode beim Einsatz besonders toleranter Turbosätze zur Anwendung, welche keine besonderen Drehzahltransienten insbesondere in Resonanzbereichen zum beschädigungsfreien Anfahren benötigen.The method according to the invention has the significant advantage that conventionally necessary and very complex coordination work between the control behavior of the steam turbine and that of the boiler can be reduced to a minimum or eliminated altogether. During the Starting process of the steam turbine, the controller of the valve position essentially takes over the pressure control of the boiler or supports this, so that an occurrence of a quick-closing criterion from a critical pressure behavior of the boiler out is highly unlikely. During this phase occurs simultaneously due to the opening of the valve or control valve an increase in the speed of the steam turbine. Shortly before reaching the synchronous speed, the specification of the setpoint for the open position of the valve is no longer dependent on the live steam pressure, but on the speed of the steam turbine, which is regularly specified as the control criterion for the speed of the setpoint synchronous speed. The time of the changeover of the control for the opening position of the valve or the speed difference to the synchronous speed can be determined depending on the system conditions, the difference is rather low, when the boiler is very sensitive to the opening of the control valve with pressure drop. Preferably, the method according to the invention is used when using particularly tolerant turbo sets, which do not require any special speed transients, especially in resonance ranges for damage-free starting.

Der vorbestimmte Differenzwert zur Synchrondrehzahl, bei der die Regelung der Ventilstellung von der Abhängigkeit vom Frischdampfdruck auf Abhängigkeit von der Drehzahl umgeschaltet wird, kann zweckmäßig zwischen 1% und 10% der Synchrondrehzahl betragen, so dass bei einer Synchrondrehzahl von 3000 U/min nach dem Erreichen einer Drehzahl von ca. 2900 U/min auf eine Drehzahlregelung umgeschaltet wird.The predetermined difference value to the synchronous speed, in which the control of the valve position is switched by the dependence on the live steam pressure depending on the speed, may suitably be between 1% and 10% of the synchronous speed, so that at a synchronous speed of 3000 rev / min after reaching A speed of about 2900 rev / min is switched to a speed control.

Das Regelkriterium während der Anfahrphase, in der die Ventilstellung von dem Frischdampfdruck abhängig gesteuert wird, ist vorzugsweise ein konstanter Frischdampfdruck von beispielsweise 2,5 bar.The control criterion during the start-up phase in which the valve position is controlled by the live steam pressure is preferably a constant live steam pressure of, for example, 2.5 bar.

Im Folgenden ist die Erfindung zum besseren Verständnis ohne Einschränkungswirkung anhand eines Ausführungsbeispiels mit Wasserdampf unter Bezugnahme auf eine Zeichnung näher erläutert. Es zeigt:

Figur 1
eine schematische Darstellung eines Systems mit erfindungsgemäßer Regelungseinheit bzw. geregelt mittels erfindungsgemäßen Verfahrens.
In the following, the invention for better understanding without restriction effect based on an embodiment with water vapor is explained in more detail with reference to a drawing. It shows:
FIG. 1
a schematic representation of a system with inventive control unit or regulated by means of the method according to the invention.

Figur 1 zeigt eine schematische Übersicht über ein Kraftwärmekopplungssystem 1 mit einer Regelung gemäß der Erfindung unter Anwendung der erfindungsgemäßen Anfahrmethode. Das Kraftwärmekopplungssystem 1 besteht im Wesentlichen aus einem Kessel B, einer Dampfturbine ST, einem Generator G, einem Kondensator Cond und einer Speisewasserpumpe PU. In dem Kessel B wird das von der Speisewasserpumpe PU auf einen Druck von etwa 3,5 bar geförderte Wasser erhitzt, verdampft und überhitzt mittels einer Wärmezufuhr QF. Der überhitzte Frischdampf gelangt über eine Frischdampfleitung FSL passierend ein Schnellschlussventil ESV und ein Stellventil CV zur Entspannung in die Dampfturbine ST, wo unter Erzeugung technischer Arbeit der Frischdampf auf Kondensatordruck entspannt wird, welche technische Arbeit einem Generator G antreibt, der die elektrische Leistung P in ein Netz GR einspeist. Während des Normalbetriebs dreht sich der Turbosatz bestehend aus Dampfturbine ST und Generator G mit einer Synchrondrehzahl nsync von 3000 U/min. In dem Kondensator Cond wird unter Abfuhr von Wärme QC der entspannte Dampf kondensiert. Das kondensierte Wasser wird von der Pumpe PU unter Aufnahme von technischer Arbeit WT auf den Kesseldruck von 3,5 bar gefördert. FIG. 1 shows a schematic overview of a cogeneration system 1 with a control according to the invention using the start-up method according to the invention. The combined heat and power system 1 consists essentially of a boiler B, a steam turbine ST, a generator G, a condenser Cond and a feedwater pump PU. In the boiler B, the water delivered by the feed water pump PU to a pressure of about 3.5 bar is heated, evaporated and superheated by means of a heat supply QF. The superheated live steam passes through a main steam line FSL passing a quick-closing valve ESV and a control valve CV to relax in the steam turbine ST, where under production of technical work, the live steam is expanded to condenser pressure which technical work drives a generator G, the electric power P in a Network GR feeds. During normal operation, the turbo set consisting of steam turbine ST and generator G rotates at a synchronous speed n sync of 3000 U / min. In the condenser Cond, the relaxed steam is condensed with the removal of heat QC. The condensed water is pumped by the pump PU receiving the technical work WT to the boiler pressure of 3.5 bar.

Die Brennstoffzufuhr QF zu dem Kessel B ist mittels eines Kesselreglers PID gesteuert, der die Zufuhr des festen Brennstoffs in Abhängigkeit von dem Frischdampfdruck PF einregelt mit dem Ziel, den Frischdampfdruck auf 3,5 bar konstant zu halten. Der Frischdampfdruck PF in der Frischdampfleitung FSL wird mittels eines Drucksensors PS gemessen. Die Stellung des Stellventils CV wird mittels eines Reglers PI geregelt. Mittels eines Drehzahlsensors NS wird die Drehzahl n des Turbosatzes aus Dampfturbine ST und Generator G gemessen. Die Drehzahl n und der Frischdampfdruck PF finden Eingang in eine Regelungseinheit CM, die unter anderem die Öffnungsstellung des Stellventils CV und die Brennstoffzufuhr QF über den Regler PI bzw. PID regelt bzw. ansteuert.The fuel supply QF to the boiler B is controlled by means of a boiler controller PID, which regulates the supply of solid fuel in response to the live steam pressure PF with the aim of keeping the live steam pressure constant at 3.5 bar. The live steam pressure PF in the Main steam line FSL is measured by means of a pressure sensor PS. The position of the control valve CV is controlled by means of a regulator PI. By means of a speed sensor NS, the speed n of the turbo set of steam turbine ST and generator G is measured. The speed n and the live steam pressure PF are input to a control unit CM, which controls or controls, among other things, the opening position of the control valve CV and the fuel supply QF via the controller PI or PID.

In einer ersten Phase des Anfahrens des Kraftwärmekopplungssystems 1 ist das Schnellschlussventil ESV geschlossen und der Kessel B erzeugt unter Brennstoffzufuhr QF Frischdampf, der unter Passage durch ein Bypassventil VR über eine Reduzierstation direkt in den Kondensator Cond eingespeist wird. Bei Erreichen nicht näher erläuteter Kriterien, z.B. Dampfreinheit oder Stabilität über ein gewissen Zeitraum, schließt das Bypassventil VR. Das Schnellschlussventil ESV öffnet gleichzeitig mit dem Schließen des Bypassventils VR und das Stellventil CV öffnet soweit, dass etwa 50% der maximalen Öffnungsstellung des Stellventils CV erreicht sind. In diesem Schritt 2 des Anfahrverfahrens fällt der Frischdampfdruck PF leicht ab und die Drehzahl n der Dampfturbine ST steigt an. Die Regelungseinheit CM regelt über den Regler PI die Öffnungsstellung des Stellventils CV derart, dass der Frischdampfdruck weitestgehend PF auf einem konstanten Sollwert gehalten wird (PF = Const, Xvalve = F(PF)). In dieser Phase regelt die Regeleinheit CM den Frischdampfdruck auf 3,5 bar mittels geeigneter Ansteuerung des Stellventils CV und die Drehzahl n der Dampfturbine ST steigt infolge an.In a first phase of the startup of the combined heat and power system 1, the quick-closing valve ESV is closed and the boiler B generates live steam under fuel supply QF, which is fed under passage through a bypass valve VR via a reducing station directly into the condenser Cond. Upon reaching unspecified criteria, such as steam purity or stability over a period of time, closes the bypass valve VR. The quick-closing valve ESV opens simultaneously with the closing of the bypass valve VR and the control valve CV opens so far that about 50% of the maximum open position of the control valve CV are reached. In this step 2 of the startup process, the live steam pressure PF drops slightly and the speed n of the steam turbine ST increases. The control unit CM regulates via the controller PI the opening position of the control valve CV such that the live steam pressure is largely maintained at a constant setpoint PF (PF = Const, X valve = F (PF)). In this phase, the control unit CM regulates the live steam pressure to 3.5 bar by means of suitable control of the control valve CV and the speed n of the steam turbine ST increases as a result.

Eine andere Ausführungsform sieht vor, dass das Stellventil zunächst schlicht in der ersten Öffnungsstellung von etwa 50% verbleibt ohne weitere Regelung des Frischdampfdrucks und auch nicht geführt von der Turbinendrehzahl n.Another embodiment provides that the control valve initially simply remains in the first open position of about 50% without further control of the live steam pressure and also not guided by the turbine speed n.

Bei Erreichung einer Grenzdrehzahl NG, die um einen bestimmten Differenzwert An unter der Synchrondrehzahl nsync liegt (nG ≥ nsync - Δn) schaltet die Regeleinheit CM von der Frischdampfdruck PF -geführten Regelung der Öffnungsstellung des Stellventils CF auf eine Drehzahl (n-geführte Regelung (Xvalve= f(n)) um. (Zeitpunkt 4 in Fig. 2). Der Generator G wird mit dem Netz GR synchronisiert und die Regeleinheit regelt in der anschließenden Phase 5 die Stellung des Stellventils CF ausschließlich in Abhängigkeit von der Drehzahl N, so dass die Synchrondrehzahl nsync= 3000 U/min als Sollwert vorgegeben ist.Upon reaching a limit speed NG, which is by a certain differential value An below the synchronous speed n sync (n G ≥ n sync - Δn), the control unit CM switches from the live steam pressure PF-guided control of the open position of the control valve CF to a speed (n-guided Control (X valve = f (n)) at (time 4 in Fig. 2 ). The generator G is synchronized with the network GR and the control unit regulates in the subsequent phase 5, the position of the control valve CF only in dependence on the speed N, so that the synchronous speed n sync = 3000 U / min is specified as the setpoint.

Claims (11)

  1. Method for starting up a steam turbine (ST) to a synchronous speed of rotation (nsync), which steam turbine (ST) is operated in a combined heat and power co-generation system (1) having a boiler (B) and at least one valve (CV) which is arranged in a steam line between the boiler (B) and the steam turbine (ST) and has a controllable open position, with a live steam pressure (PF) being measured upstream of the valve (CV), characterised by:
    a) opening of the valve (CV) to a first open position during a startup operation of the steam turbine (ST), wherein after the opening of the valve (CV) to the first open position the open position of the valve (CV) is controlled as a function of the live steam pressure (PF) in such a way that the fresh steam pressure (PF) does not fall below a first lower limit,
    b) switchover of the control of the open position of the valve (CV) to a dependence on the speed of rotation (N) if the speed of rotation (N) of the steam turbine (ST) has approached the synchronous speed of rotation (nsync) except for a predetermined first differential value (Δn),
    c) control of the open position of the valve (CV) in such a way that the steam turbine (ST) rotates at the synchronous speed of rotation (nsync).
  2. Method according to claim 1,
    characterised in that the first open position is equal to between 25% and 75%.
  3. Method according to claim 1 or 2,
    characterised in that before the control of the open position of the valve (CV) is switched over to a dependence on the speed of rotation (N) the open position is controlled by the controller to the constant setpoint value of the first open position.
  4. Method according to claim 1, 2 or 3,
    characterised in that
    the first differential value (Δn) is equal to between one percent and twenty percent of the synchronous speed of rotation (nsync).
  5. Method according to claim 1, 2, 3, or 4,
    characterised in that
    a setpoint value of the live steam pressure (PF) is constant prior to the second step (step b)).
  6. Method according to claim 1, 2, 3, 4 or 5,
    characterised in that
    during or after the opening of the control valve (CV) a bypass valve (VR) for bypassing the steam turbine (ST) is fully closed, with the result that the steam from the boiler (B) completely passes the steam turbine (ST).
  7. Control module (CM) of a combined heat and power co-generation system (1), which combined heat and power co-generation system (1) has a boiler and at least one steam turbine (ST) that is to be operated at a synchronous speed of rotation (nsync), wherein at least one valve (CV) arranged in a steam line (FSL) and having a controllable open position is provided between the steam turbine (ST) and the boiler (B), with a live steam pressure (PF) being measured upstream of the valve (CV),
    characterised in that
    the control module (CM) is embodied in such a way that
    a) in a first step of the startup of the combined heat and power co-generation system (1) the valve (CV) opens and after the first step during the startup operation of the steam turbine the open position of the valve (CV) is controlled as a function of the measured live steam pressure (PF) in such a way that the live steam pressure (PF) does not fall below a first lower limit,
    b) in a second step the control of the open position of the valve (CV) is switched over to a dependence on the speed of rotation (n) if the speed of rotation (n) of the steam turbine (ST) has approached the synchronous speed of rotation (nsync) except for a predetermined differential value (Δn), and
    c) in a third step the open position of the valve (CV) is controlled in such a way that the steam turbine (ST) rotates at the synchronous speed of rotation (nsync).
  8. Control module (CM) according to claim 7,
    characterised in that the control module (CM) is embodied in such a way that
    the first open position is equal to between 25% and 75%.
  9. Control module (CM) according to claim 7 or 8,
    characterised in that the control module (CM) is embodied in such a way that
    the first differential value (Δn) is equal to between one percent and twenty percent of the synchronous speed of rotation (nsync).
  10. Control module (CM) according to claim 7, 8 or 9,
    characterised in that the control module (CM) is embodied in such a way that
    in the first step a setpoint value of the live steam pressure (PF) is constant.
  11. Control module (CM) according to claim 7, 8, 9 or 10,
    characterised in that the control module (CM) is embodied in such a way that
    during or after the opening of the control valve (CV) a bypass valve (VR) for bypassing the steam turbine (ST) is fully closed, with the result that the steam from the boiler (B) completely passes the steam turbine (ST).
EP07014816.8A 2007-07-27 2007-07-27 Start-up of a steam turbine Active EP2037086B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP07014816.8A EP2037086B1 (en) 2007-07-27 2007-07-27 Start-up of a steam turbine
PL07014816T PL2037086T3 (en) 2007-07-27 2007-07-27 Start-up of a steam turbine
PCT/EP2008/059241 WO2009016029A2 (en) 2007-07-27 2008-07-15 Starting of a steam turbine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07014816.8A EP2037086B1 (en) 2007-07-27 2007-07-27 Start-up of a steam turbine

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EP2037086A1 EP2037086A1 (en) 2009-03-18
EP2037086B1 true EP2037086B1 (en) 2013-05-15

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Publication number Priority date Publication date Assignee Title
US9249691B2 (en) * 2012-01-06 2016-02-02 General Electric Company Systems and methods for cold startup of rankine cycle devices
US20160208656A1 (en) * 2013-08-28 2016-07-21 Siemens Aktiengesellschaft Operating method for an externally heated forced-flow steam generator

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4258424A (en) 1972-12-29 1981-03-24 Westinghouse Electric Corp. System and method for operating a steam turbine and an electric power generating plant
US3879616A (en) * 1973-09-17 1975-04-22 Gen Electric Combined steam turbine and gas turbine power plant control system
US4329592A (en) 1980-09-15 1982-05-11 General Electric Company Steam turbine control
US4598551A (en) * 1985-10-25 1986-07-08 General Electric Company Apparatus and method for controlling steam turbine operating conditions during starting and loading

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EP2037086A1 (en) 2009-03-18
WO2009016029A2 (en) 2009-02-05
WO2009016029A3 (en) 2009-04-02
PL2037086T3 (en) 2013-10-31

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