EP3475539A1 - Method for the short-term adjustment of the output of a combined-cycle power plant steam turbine, for primary frequency control - Google Patents

Method for the short-term adjustment of the output of a combined-cycle power plant steam turbine, for primary frequency control

Info

Publication number
EP3475539A1
EP3475539A1 EP17780006.7A EP17780006A EP3475539A1 EP 3475539 A1 EP3475539 A1 EP 3475539A1 EP 17780006 A EP17780006 A EP 17780006A EP 3475539 A1 EP3475539 A1 EP 3475539A1
Authority
EP
European Patent Office
Prior art keywords
pressure
steam
turbine
water
mass flow
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Withdrawn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
EP17780006.7A
Other languages
German (de)
French (fr)
Inventor
Zsuzsa Preitl
Frank Thomas
Bernd Weissenberger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens Energy Global GmbH and Co KG
Original Assignee
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
Publication of EP3475539A1 publication Critical patent/EP3475539A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/101—Regulating means specially adapted therefor
    • 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
    • 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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/18—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbine being of multiple-inlet-pressure type
    • F01K7/20—Control means specially adapted therefor
    • 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
    • F05D2220/70—Application in combination with
    • F05D2220/72—Application in combination with a steam turbine
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • the invention relates to a method for short-term power adjustment of a steam turbine of a gas and steam power ⁇ plant for the primary control.
  • a steam turbine of a gas and steam power ⁇ plant for the primary control.
  • the object of the invention is therefore to provide a method for short-term power adjustment of a steam turbine of a gas and steam power plant for the primary control.
  • the method according to the invention for short-term power adaptation of a steam turbine of a gas and steam power plant for the primary control comprises the following steps:
  • Pressure measurement which measures upstream of the accumulated turbine valve the pressure of the steam mass flow flowing into the at least one pressure stage
  • the at least proporti ⁇ onal acting controller can in this case be, for example, a P, advantageously a PID or PI controller.
  • a rapid measure namely the opening of a throttled turbine valve with a long-acting measure, namely the increase of the injection quantity or the feedwater mass flow is thus combined.
  • a rapid measure namely the opening of a throttled turbine valve with a long-acting measure, namely the increase of the injection quantity or the feedwater mass flow is thus combined.
  • at least one turbine valve must be sufficiently throttled. If additional power is required, an increased mass flow through the steam turbine can be made available under these circumstances by opening the at least one throttled turbine valve via a pressure discharge. It is well known that this happens relatively quickly, and thus this measure is ideally suited to the speed requirements with regard to primary control reserve. However, it is also known that with acceptable throttle levels of the turbine valves, this measure is very limited in time.
  • the one measure namely the opening of the at least one throttled turbine valve
  • a further measure namely the increase in the injections or the feedwater mass flow.
  • the opening of the at least one turbine valve provides here for the rapid and increasing the injections or the feedwater quantity for a long-lasting increase in power of the steam turbine, which he ⁇ wished in particular in the case of Primarregelreserve.
  • the invention can be practically implemented by providing the additionally requested power by opening at least one turbine valve, for example in the form of a kind of power control of the steam turbine. However, this immediately reduces the vapor pressure of the corresponding pressure stage (the accumulator "empties" itself). However, by also "tapping" the thermal energy store by increasing the injection quantity or feed water quantity, the decrease of the vapor pressure can be efficiently counteracted. If, on the other hand, the vapor pressure increases in the opposite case
  • varying power outputs of the steam turbine via different opening degrees of the turbine valve of Pressure stage and the associated changes in injection or feed water quantity in the high-pressure stage for pressure support of the medium-pressure stage is no longer directly coupled together, which has further stabilizing effect.
  • a particularly high level of flexibility is achieved when introducing a variable water content, and the opening be as close relationship ⁇ for turbine valves in a plurality of pressure stages of the steam turbine takes place.
  • ⁇ for turbine valves in a plurality of pressure stages of the steam turbine takes place.
  • FIG. ⁇ shows schematically a section of a gas and steam power plant with a high-pressure ⁇ stage 1, a medium-pressure stage 2, and two Niederdruckstu- fen 3 and 4 of a steam turbine. All stages 1 to 4 are here connected to each other via a rotor axis.
  • an intermediate-pressure drum does not further shown can be used as additional steam ⁇ memory here and on the other has been shown in a high-pressure side throttling that by the associated interplay of an altered ⁇ Stammsstel- development of the high pressure turbine valve 51 and a modified
  • the pressure control is no longer done via the turbine valve but only via the change in the injection.
  • limits must also be met here, that is, the steam temperature can not be reduced or increased above a certain level, bezie ⁇ tion can not be closed when the injection is closed, etc.
  • the power control takes place via the components 21, 46, 47, 42, 33 and the turbine valve 31 of the supply to the medium-pressure stage, while via the pressure control for stabilization mainly via the components 32, 41, 48, 45, 49, 100, 110, 72, 71 and the injection 73, which is preferably downstream of a high-pressure superheater heating surface, not shown here, in the supply to the high-pressure stage.
  • control device 100 not only the injection quantity for the high-pressure stage 1, but at the same time the injection quantity for the medium-pressure stage 2 itself via the components 120, 81, 82 and the injection 83, which also preferably a not shown here intermediate ⁇ hitzerterrorism Structure downstream pressure stabilizing re ⁇ gelt.
  • This has the advantage that in addition to the use of the Metal masses of the high-pressure stage 1 stored thermal energy, even the stored in such reheater heating thermal energy for pressure support ago ⁇ can be tightened.
  • the operation is controlled by the turbine valve 31 of the medium-pressure stage 2.
  • the rotor via a Messeinrich ⁇ device 21, the current output of the steam turbine and with ermit ⁇ telt an associated power set point, always adjust itself depending on the required primary control reserve as ⁇ the can, compared.
  • an additional modified introduction of a variable proportion of water in the Steam mass flow for the Mitteldruckstu ⁇ Fe 2 is provided by means of the injection cooling 83, which is also advantageously realized as an intermediate injection device of a reheater not shown here in detail rt 41 compared with a pressure measurement 32 of the steam mass flow.
  • the pressure measurement 32 is performed here upstream of the attached jam ⁇ th turbine valve 31 as soon as the desired pressure value is exceeded 41 under- be ⁇ relationship instance, the opening takes place rela ⁇ hung as closing the inlets 71 and 81 via corresponding control systems 72 and 82, so that a modified Water content is supplied to the injection cooling 73 and 83.
  • This variable proportion of water is introduced into the steam mass stream until an adjusted steam temperature setpoint value 49 is reached.
  • This is determined in the present example the difference between a predetermined Dampftempera- tur groundsollives 45 and acting the output of a proportio nal ⁇ -integral (PI) controller 48 which evaluates the difference between the pressure measurement 32 and pressure setpoint 41 and compensates for ⁇ .
  • PI controller 48 In the subsequent control device 100 is DIE ser temporally variable steam temperature set value 49 determined as changed ⁇ derliche input variable for the Dampftemperaturregelungsein- device 100 and used.
  • the PI controller 48 could just as a simple P-controller or a PID controller or other, equivalent acting regulator can be used, in the present example, the PI controller has proved advantageous.

Abstract

The invention relates to a method for the short-term adjustment of the output of a steam turbine of a combined-cycle power plant, for primary frequency control, comprising the steps of: opening, respectively closing, a backed-up turbine valve (31, 51) of at least one pressure stage (1, 2, 3, 4) of the steam turbine, according to a required change in output; comparing a specified desired pressure (41) with a pressure measurement (32) which is carried out upstream of the backed-up turbine valve (31) to measure the pressure of the steam mass flow flowing into the at least one pressure stage (1, 2, 3, 4); and opening, respectively closing, a feed line (71, 81) for introducing a variable proportion of water into the steam mass flow of at least one of the pressure stages (1, 2, 3, 4) as soon as the pressure falls below or exceeds the desired pressure (41); the variable proportion of water is introduced into the steam mass flow until an adjusted desired steam temperature (49) is reached, which is determined from the difference between a basic specified desired steam temperature (45) and the default value of a controller (48) which operates at least proportionally and evaluates the difference between the pressure measurement (32) and the desired pressure (41).

Description

Beschreibung description
Verfahren zur kurzfristigen Leistungsanpassung einer Dampfturbine eines Gas-und Dampfkraftwerks für die Primärregelung Method for short-term power adaptation of a steam turbine of a gas and steam power plant for primary control
Die Erfindung betrifft ein Verfahren zur kurzfristigen Leistungsanpassung einer Dampfturbine eines Gas- und Dampfkraft¬ werks für die Primärregelung. So wie beispielsweise auch aus der DE 10 2010 040 623 AI bekannt. The invention relates to a method for short-term power adjustment of a steam turbine of a gas and steam power ¬ plant for the primary control. For example, as known from DE 10 2010 040 623 AI.
Von modernen Kraftwerken werden nicht nur hohe Wirkungsgrade gefordert, sondern auch eine möglichst flexible Betriebswei¬ se. Hierzu gehört außer kurzen Anfahrzeiten und hohen Laständerungsgeschwindigkeiten auch die Möglichkeit, Frequenzstö- rungen im Netz auszugleichen. Um diese Anforderungen zu erfüllen, muss das Kraftwerk in der Lage sein, Mehrleistungen von beispielsweise fünf Prozent und mehr innerhalb weniger Sekunden zur Verfügung zu stellen und diese Mehrleistung dann für einen geforderten MindestZeitraum von beispielsweise 15 Minuten zu gewährleisten. Of modern power plants not only high efficiencies are required, but also the most flexible Betriebswei ¬ se. This includes except short start and high load change speeds also the possibility Frequenzstö- conclusions on the net balance. To meet these requirements, the power plant must be able to provide more power of, for example, five percent or more within a few seconds, and then provide this extra power for a required minimum period of, for example, 15 minutes.
Dies wird in einem gewöhnlichen Gas- und Dampfkraftwerk üblicherweise durch eine Lasterhöhung der Gasturbine realisiert. Unter gewissen Umständen kann es aber insbesondere im oberen Lastbereich besonders günstig sein, den gewünschten Leistungsanstieg nicht ausschließlich durch die Gasturbine, son¬ dern auch durch eine adäquate Einbindung des die Dampfturbine speisenden Wasser-Dampfkreislaufs bereitzustellen. Daher werden in jüngerer Zeit wieder vermehrt Lösungen verfolgt, bei denen die Dampfturbine ebenfalls einen zusätzlichen Beitrag zur Frequenzstützung leisten kann und soll. Normalerweise kommen hier dann Verfahren zum Einsatz die einerseits in keinen zusätzlichen Investitionskosten münden (z.B. durch den Bedarf zusätzlicher Komponenten) und andererseits den gewöhn- liehen Anlagenbetrieb nicht negativ beeinträchtigen, z.B. Wirkungsgradverlust im Stationärbetrieb. In diesem Zusammenhang wurden in der jüngeren Vergangenheit Lösungen für Abhitzedampferzeuger entwickelt, die im Wesentlichen, die in den Metallmassen der Heizflächen gespeicherte thermische Energie geeignet nutzen. Dies erfolgt hauptsäch- lieh durch schnelle Änderungen der Stellgrößen Speisewasser bzw. Einspritzwasser. This is usually realized in a conventional gas and steam power plant by increasing the load of the gas turbine. But under certain circumstances it may be particularly favorable, particularly in the upper load range to provide the desired increase in power not only by the gas turbine, son ¬ countries by an adequate involvement of the steam turbine supplying water-steam cycle. Therefore, more solutions are being pursued more recently, in which the steam turbine can and should also make an additional contribution to the frequency support. Normally, processes are then used which, on the one hand, result in no additional investment costs (eg due to the need for additional components) and, on the other hand, do not adversely affect the usual plant operation, eg loss of efficiency in steady-state operation. In this connection, solutions for heat recovery steam generators have been developed in the recent past, which essentially make appropriate use of the thermal energy stored in the metal masses of the heating surfaces. This is done mainly by rapid changes of the manipulated variables feed water or injection water.
Über weitergehende theoretische Untersuchungen hat sich nun herausgestellt, dass durch die Nutzung des oben genannten thermischen Speichers zwar ein vergleichsweise großes Sekun- denreservepotenzial besteht, dieses aber nur relativ zeitver¬ zögert bzw. träge abgerufen werden kann. Hinsichtlich der Primarregelreserve, bei der per Definition auf schnelle Ände¬ rungen der Netzfrequenz reagiert werden muss, sind solche Maßnahmen aber nicht vollständig geeignet. On further theoretical studies has now been found that a relatively large secondary is through the use of the aforementioned thermal storage while denreservepotenzial, but this relatively zeitver ¬ hesitates and can be accessed sluggish. With regard to the primary control reserve, in the need to respond by definition on fast Ände ¬ conclusions of the line frequency, such measures are not fully suitable.
Aufgabe der Erfindung ist es daher, ein Verfahren zur kurzfristigen Leistungsanpassung einer Dampfturbine eines Gas- und Dampfkraftwerks für die Primärregelung bereitzustellen. The object of the invention is therefore to provide a method for short-term power adjustment of a steam turbine of a gas and steam power plant for the primary control.
Diese Aufgabe wird mit dem Verfahren gemäß den Merkmalen des Anspruchs 1 gelöst. This object is achieved by the method according to the features of claim 1.
Das erfindungsgemäße Verfahren zur kurzfristigen Leistungsan- passung einer Dampfturbine eines Gas- und Dampfkraftwerks für die Primärregelung umfasst dabei folgende Schritte: The method according to the invention for short-term power adaptation of a steam turbine of a gas and steam power plant for the primary control comprises the following steps:
- Öffnen beziehungsweise Schließen eines angestauten Turbinenventils, zumindest einer Druckstufe der Dampfturbine, in Abhängigkeit von einer geforderten Leistungsänderung, - Vergleich eines vorgegebenen Drucksollwerts mit einer  - Opening or closing a pent-up turbine valve, at least one pressure stage of the steam turbine, in dependence on a required change in performance, - Comparison of a predetermined pressure setpoint with a
Druckmessung, die stromaufwärts vom angestauten Turbinenventil den Druck des in die zumindest eine Druckstufe ein¬ strömenden Dampfmassenstroms misst, Pressure measurement, which measures upstream of the accumulated turbine valve the pressure of the steam mass flow flowing into the at least one pressure stage,
- Öffnen beziehungsweise Schließen einer Zuführung zum Ein- bringen eines variablen Wasseranteils in den Dampfmassenstrom zumindest einer der Druckstufen sobald der Drucksollwert unter- beziehungsweise überschritten wird, - wobei der variable Wasseranteil solange in den Dampfmassen¬ strom eingebracht wird, bis ein angepasster Dampftempera- tursollwert erreicht ist, der sich aus der Differenz eines vorgegebenen Dampftemperaturgrundsollwertes und dem Aus- gangswert eines zumindest proportional wirkenden Reglers, welcher die Differenz aus Druckmessung und Drucksollwert auswertet und ausgleicht, bestimmt. Der zumindest proporti¬ onal wirkende Regler kann dabei zum Beispiel ein P-, PID- oder vorteilhafterweise ein PI-Regler sein. Opening or closing a feed for introducing a variable proportion of water into the steam mass flow of at least one of the pressure stages as soon as the pressure setpoint is undershot or exceeded, - Wherein the variable water content is introduced into the steam mass stream until an adjusted steam temperature setpoint is reached, which is the difference between a predetermined basic steam temperature setpoint and the output value of an at least proportionally acting controller, which evaluates the difference between pressure measurement and pressure setpoint and compensates, certainly. The at least proporti ¬ onal acting controller can in this case be, for example, a P, advantageously a PID or PI controller.
Gerade bei der Anforderung von zusätzlicher Leistung für die Primärregelung wird somit eine schnelle Maßnahme, nämlich das Öffnen eines angedrosselten Turbinenventils mit einer lange wirkenden Maßnahme, nämlich der Erhöhung der Einspritzmenge bzw. des Speisewassermassenstroms kombiniert. Hier erfolgt also eine Kombination aus Leistungsregelung für schnelle Leistungsanpassung und Druckstützung während der Leistungsanpassung. Dazu muss zumindest ein Turbinenventil ausreichend angedrosselt sein. Wird nun zusätzliche Leistung benötigt, kann unter diesen Umständen durch Öffnen des zumindest einen angedrosselten Turbinenventils über eine Druckentladung ein erhöhter Massenstrom durch die Dampfturbine zur Verfügung gestellt werden. Es ist allgemein bekannt, dass dies relativ zügig geschieht, und sich diese Maßnahme somit bestens für die Schnelligkeitsanforderungen hinsichtlich Primarregelre- serve eignet. Es ist aber auch bekannt, dass bei akzeptablen Androsselgraden der Turbinenventile diese Maßnahme sehr stark zeitlich limitiert ist. Und genau hier setzt nun die vorlie¬ gende Erfindung an. Bei entsprechender Anforderung an zusätz- licher Leistung wird die eine Maßnahme, nämlich das Öffnen des zumindest einen angedrosselten Turbinenventils mit einer weiteren Maßnahme, nämlich der Erhöhung der Einspritzungen bzw. des Speisewassermassenstroms, kombiniert. Das Öffnen des zumindest einen Turbinenventils sorgt hier für die schnelle und das Erhöhen der Einspritzungen bzw. der Speisewassermenge für eine lang anhaltende Leistungssteigerung der Dampfturbine, was insbesondere im Falle der Primarregelreserve er¬ wünscht ist. Praktisch umsetzbar wird die Erfindung, indem die zusätzlich angefragte Leistung durch Öffnen zumindest eines Turbinenventils, zum Beispiel in Form einer Art Leistungsregelung der Dampfturbine bereitgestellt wird. Hierdurch reduziert sich allerdings unmittelbar der Dampfdruck der entsprechenden Druckstufe (der Speicher „entleert" sich) . Indem aber nun durch Erhöhung der Einspritzmenge bzw. der Speisewassermenge auch der thermische Energiespeicher „angezapft" wird, kann dem Abfall des Dampfdrucks effizient entgegengewirkt werden. Steigt hingegen im umgekehrten Fall der Dampfdruck beim Especially in the demand for additional power for the primary control, a rapid measure, namely the opening of a throttled turbine valve with a long-acting measure, namely the increase of the injection quantity or the feedwater mass flow is thus combined. Here is a combination of power control for fast power adjustment and pressure support during power adjustment. For this purpose, at least one turbine valve must be sufficiently throttled. If additional power is required, an increased mass flow through the steam turbine can be made available under these circumstances by opening the at least one throttled turbine valve via a pressure discharge. It is well known that this happens relatively quickly, and thus this measure is ideally suited to the speed requirements with regard to primary control reserve. However, it is also known that with acceptable throttle levels of the turbine valves, this measure is very limited in time. And right here now of the products contained ¬ constricting invention comes in. With a corresponding requirement for additional power, the one measure, namely the opening of the at least one throttled turbine valve, is combined with a further measure, namely the increase in the injections or the feedwater mass flow. The opening of the at least one turbine valve provides here for the rapid and increasing the injections or the feedwater quantity for a long-lasting increase in power of the steam turbine, which he ¬ wished in particular in the case of Primarregelreserve. The invention can be practically implemented by providing the additionally requested power by opening at least one turbine valve, for example in the form of a kind of power control of the steam turbine. However, this immediately reduces the vapor pressure of the corresponding pressure stage (the accumulator "empties" itself). However, by also "tapping" the thermal energy store by increasing the injection quantity or feed water quantity, the decrease of the vapor pressure can be efficiently counteracted. If, on the other hand, the vapor pressure increases in the opposite case
Schließen des Turbinenventils an (das Ventil schließt bei ge¬ ringerer Leistungsanforderung des Netzes) , so kann durch die Reduzierung der Einspritzmengen bzw. des Speisewassermassen- Stroms der Druckerhöhung ebenfalls effektiv entgegengewirkt werden. Der DampfSpeicher wirkt somit als Pufferglied für die in den Metallmassen gespeicherte thermische Energie, so dass trotz ihres trägen Verhaltens bei der Freisetzung diese ge¬ speicherte Energie bei der Primärregelreserve über den Umweg des „schnellen" DampfSpeichers eingesetzt werden kann. Closing of the turbine valve (the valve closes at ge ¬ ringerer power requirement of the network), so can be effectively counteracted by reducing the injection quantities or the feedwater mass flow of pressure increase. The steam storage thus acts as a buffer member for the stored thermal energy in the metal masses, so that despite their sluggish behavior during release this ge ¬ stored energy at the primary control reserve via the detour of the "fast" steam storage can be used.
Als besonders vorteilhaft hat sich herausgestellt, wenn das Öffnen beziehungsweise Schließen am Turbinenventil der Mit¬ teldruckstufe der Dampfturbine erfolgt. Hierdurch kann zu- sätzlich der DampfSpeicher in der Trommel der Mitteldruckstufe genutzt werden. Es hat sich gezeigt, dass die Androsselung der Mitteldruckstufe im Gegensatz zu einer Androsselung der Hochdruckstufe hinsichtlich möglicher Schwingungsneigung wesentlich unempfindlicher ist. Particularly advantageous has been found when opening or closing the turbine valve With ¬ teldruckstufe done the steam turbine. As a result, the steam reservoir in the drum of the medium-pressure stage can additionally be used. It has been shown that the throttling of the medium-pressure stage, in contrast to a throttling of the high pressure stage with respect to possible tendency to vibration is much less sensitive.
Vorzugsweise wird diese Androsselung der Mitteldruckstufe da¬ durch ergänzt, dass das Zuführen eines variablen Wasseranteils in den in die Hochdruckstufe der Dampfturbine einströ¬ menden Dampfmassenstrom erfolgt. Bei einer solchen Kombinati- on von Druckstützung auf Seiten der Hochdruckstufe und einer Leistungsregelung ausschließlich auf Seiten der Mitteldruckstufe sind variierende Leistungsabgaben der Dampfturbine über unterschiedliche Öffnungsgrade des Turbinenventils der Mit- teldruckstufe und die damit verknüpften Änderungen der Einspritz- bzw. Speisewassermenge in der Hochdruckstufe zur Druckstützung der Mitteldruckstufe nicht mehr unmittelbar miteinander gekoppelt, was sich weiter stabilisierend aus- wirkt. Preferably, this throttling of the medium-pressure stage since ¬ supplemented by that the supplying a variable proportion of water in the einströ ¬ Menden in the high pressure stage of the steam turbine steam mass flow takes place. In such a combination of pressure support on the high-pressure stage side and power control exclusively on the medium-pressure stage side, varying power outputs of the steam turbine via different opening degrees of the turbine valve of Pressure stage and the associated changes in injection or feed water quantity in the high-pressure stage for pressure support of the medium-pressure stage is no longer directly coupled together, which has further stabilizing effect.
Eine besonders hohe Flexibilität wird dann erreicht, wenn das Einbringen eines variablen Wasseranteils und das Öffnen be¬ ziehungsweise Schließen von Turbinenventilen in mehreren der Druckstufen der Dampfturbine erfolgt. Letztendlich wird aber von Fall zu Fall zu entscheiden sein, welche Kombinationsmög¬ lichkeiten für welches Änderungsprofil am sinnvollsten sind. Für jede Kraftwerksanlage ist individuell vor dem Hintergrund der Netz- und Kundenanforderungen sowie vorhandener Designre- serven festzulegen, welche Druckstufe inwieweit anzudrosseln und zu kühlen ist. A particularly high level of flexibility is achieved when introducing a variable water content, and the opening be as close relationship ¬ for turbine valves in a plurality of pressure stages of the steam turbine takes place. Ultimately, however, be determined case by case, which Kombinationsmög ¬ possibilities are for which change profile makes the most sense. For each power plant, it must be individually determined, against the background of grid and customer requirements as well as existing design reserves, which pressure level is to be throttled and cooled to what extent.
Weitere bevorzugte Ausführungen der vorliegenden Erfindung sind den Unteransprüchen zu entnehmen. Further preferred embodiments of the present invention can be found in the subclaims.
Die Erfindung soll nachfolgend anhand einer Figur beispiel¬ haft erläutert werden. Die Figur zeigt schematisch einen Ausschnitt eines Gas- und Dampfkraftwerks mit einer Hochdruck¬ stufe 1, einer Mitteldruckstufe 2, sowie zwei Niederdruckstu- fen 3 und 4 einer Dampfturbine. Alle Stufen 1 bis 4 sind hier über eine Rotorachse miteinander verbunden. The invention will be explained by way of example with reference to a figure ¬ . The figure shows schematically a section of a gas and steam power plant with a high-pressure ¬ stage 1, a medium-pressure stage 2, and two Niederdruckstu- fen 3 and 4 of a steam turbine. All stages 1 to 4 are here connected to each other via a rotor axis.
Wie sich in dynamischen Simulationen gezeigt hat, kann es von besonderem Vorteil sein, das Turbinenventil 31 für die Mit- teldruckstufe 2 anzudrosseln. Zum einen kann hier eine nicht näher dargestellte Mitteldrucktrommel als zusätzlicher Dampf¬ speicher genutzt werden und zum anderen hat sich bei einer hochdruckseitigen Androsselung gezeigt, dass durch das damit verbundene Zusammenspiel aus einer veränderten Öffnungsstel- lung des Hochdruck-Turbinenventils 51 und einem verändertenAs has been shown in dynamic simulations, it may be of particular advantage to throttle the turbine valve 31 for the intermediate pressure stage 2. Firstly, an intermediate-pressure drum does not further shown can be used as additional steam ¬ memory here and on the other has been shown in a high-pressure side throttling that by the associated interplay of an altered Öffnungsstel- development of the high pressure turbine valve 51 and a modified
Hochdruck-Dampfmassenstrom als Resultat der veränderten Hochdruck-Speisewasser- und Hochdruck-Einspritzmenge, die Hoch¬ druckstufe sich hinsichtlich Schwingungsneigungen wesentlich empfindlicher verhält. Dagegen wirkt sich bei einer ausschließlichen Androsselung der Mitteldruckstufe 2 über unterschiedliche Öffnungsgrade des Turbinenventils 31 der Mittel¬ druckstufe und einer über die Regelung 100 mittelbar damit verknüpfte Änderungen der Einspritz- und Speisewassermenge der Hochdruckstufe 1 insgesamt stabilisierend aus, da beide Maßnahmen nicht auf die gleiche Druckstufe wirken und somit nicht mehr unmittelbar miteinander gekoppelt sind. Der Kerngedanke der vorliegenden Erfindung besteht somit darin, eine Leistungsregelung über die Stellung eines Turbinenventils mit einer Druckregelung über die Erhöhung bzw. Reduzierung der Einspritzmenge zu kombinieren. Damit existieren quasi zwei Regelkreise. Das heißt, die Druckregelung erfolgt nicht mehr über das Turbinenventil sondern nur über die Veränderung der Einspritzung. Selbstverständlich müssen auch hier Grenzen eingehalten werden, das heißt, die Dampftemperatur kann nicht über ein bestimmtes Maß reduziert oder erhöht werden, bezie¬ hungsweise kann bei geschlossener Einspritzung diese nicht weiter zugefahren werden, etc.. High-pressure steam mass flow as a result of the changed high-pressure feedwater and high-pressure injection quantity, the high ¬ pressure level significantly in terms of vibration inclinations more sensitive behaves. In contrast, with an exclusive throttling of the medium-pressure stage 2 via different degrees of opening of the turbine valve 31 of the middle ¬ pressure stage and indirectly via the control 100 associated changes in the injection and feed water quantity of the high pressure stage 1 has a total stabilizing effect, since both measures are not on the same pressure level act and are therefore no longer directly linked to each other. The core idea of the present invention is thus to combine a power control via the position of a turbine valve with a pressure control via the increase or reduction of the injection quantity. There are thus two control loops. That is, the pressure control is no longer done via the turbine valve but only via the change in the injection. Of course, limits must also be met here, that is, the steam temperature can not be reduced or increased above a certain level, bezie ¬ tion can not be closed when the injection is closed, etc.
Das in der Figur dargestellte Ausführungsbeispiel zeigt darü¬ ber hinaus, dass verschiedene Kombinationen denkbar sind. So erfolgt in der hier gezeigten Ausführung die Leistungsregelung über die Komponenten 21, 46, 47, 42, 33 und das Turbi- nenventil 31 der Zuführung zur Mitteldruckstufe, während über die Druckregelung zur Stabilisierung hauptsächlich über die Komponenten 32, 41, 48, 45, 49, 100, 110, 72, 71 und die Einspritzung 73, welcher vorzugsweise noch eine hier nicht näher dargestellte Hochdrucküberhitzerheizfläche nachgeschal- tet ist, in der Zuführung zur Hochdruckstufe erfolgt. Zudem kann es wie im vorliegenden Ausführungsbeispiel dargestellt, vorteilhaft sein, wenn die Regeleinrichtung 100 nicht nur die Einspritzmenge für die Hochdruckstufe 1, sondern gleichzeitig die Einspritzmenge für die Mitteldruckstufe 2 selbst über die Komponenten 120, 81, 82 und die Einspritzung 83, welcher auch vorzugsweise eine hier nicht näher dargestellte Zwischenüber¬ hitzerheizfläche nachgeschaltet ist, druckstabilisierend re¬ gelt. Dies hat den Vorteil, dass neben der Nutzung der in den Metallmassen der Hochdruckstufe 1 gespeicherten thermischen Energie, auch die in einem solchen Zwischenüberhitzerheiz- system gespeicherte thermische Energie zur Druckstützung her¬ angezogen werden kann. Unter diesen Umständen kann entweder bei gleicher Bauteilbelastung der Hochdruckstufe über einen längeren Zeitraum eine Primärregelreserve bereitgestellt werden, beziehungsweise bei gleicher Zeitdauer der Primärre¬ gelreserve die Änderung der Dampftemperatur der Hochdruckstufe reduziert werden, was in einer Reduzierung der Bauteilbe- lastung der Hochdruckstufe resultiert. Auch könnte natürlich mit eigenen Vor - bzw. Nachteilen behaftet, die Leistungsre¬ gelung über eines der anderen Turbinenventile realisiert wer¬ den, unabhängig davon, welche Einspritzung zur Druckstabilisierung verwendet wird. The embodiment shown in the figure shows darü ¬ beyond that various combinations are conceivable. Thus, in the embodiment shown here, the power control takes place via the components 21, 46, 47, 42, 33 and the turbine valve 31 of the supply to the medium-pressure stage, while via the pressure control for stabilization mainly via the components 32, 41, 48, 45, 49, 100, 110, 72, 71 and the injection 73, which is preferably downstream of a high-pressure superheater heating surface, not shown here, in the supply to the high-pressure stage. In addition, as shown in the present embodiment, it may be advantageous if the control device 100 not only the injection quantity for the high-pressure stage 1, but at the same time the injection quantity for the medium-pressure stage 2 itself via the components 120, 81, 82 and the injection 83, which also preferably a not shown here intermediate ¬ hitzerheizfläche downstream pressure stabilizing re ¬ gelt. This has the advantage that in addition to the use of the Metal masses of the high-pressure stage 1 stored thermal energy, even the stored in such reheater heating thermal energy for pressure support ago ¬ can be tightened. Under these circumstances, either with the same component load of the high-pressure stage over a longer period a primary control reserve can be provided, or for the same period of Primärre ¬ gelreserve the change in steam temperature of the high-pressure stage can be reduced, resulting in a reduction of the component load of the high-pressure stage. Also, of course, could have its own advantages or disadvantages, the Leistungsre ¬ gelation realized on one of the other turbine valves who ¬ the, regardless of which injection is used for pressure stabilization.
Die Leistungsreglung erfolgt über das Turbinenventil 31 der Mitteldruckstufe 2. Dazu wird am Rotor über eine Messeinrich¬ tung 21 die aktuelle Leistungsabgabe der Dampfturbine ermit¬ telt und mit einem zugehörigen Leistungs-Sollwert, der sich in Abhängigkeit der geforderten Primärregelreserve immer wie¬ der neu einstellen kann, verglichen. Im Fall einer Differenz zwischen beiden Werten - was einer „geforderten Leistungsänderung" entspricht - findet dann eine zielgerichtete Anpas¬ sung der Öffnungsstellung des Turbinenventils 31 statt, und zwar so, dass am Ende Soll- und Istwert wieder identisch sind. Die Druckregelung erfolgt im Wesentlichen durch veränderte Einbringung eines variablen Wasseranteils in den Dampfmassenstrom für die Hochdruckstufe 1 mittels der Einspritzkühlung 73, welche vorteilhafterweise als Zwischeneinspritz- einrichtung einer hier nicht näher dargestellten Hochdruck- Überhitzerheizfläche realisiert ist. Optional ist hier ergän¬ zend eine zusätzliche veränderte Einbringung eines variablen Wasseranteils in den Dampfmassenstrom für die Mitteldruckstu¬ fe 2 mittels der Einspritzkühlung 83 vorgesehen, welche auch vorteilhafterweise als Zwischeneinspritzeinrichtung einer hier nicht näher dargestellten Zwischenüberhitzerheizfläche realisiert ist. Dazu wird ein vorgegebener Drucksollwert 41 mit einer Druckmessung 32 des Dampfmassenstroms verglichen. Die Druckmessung 32 erfolgt hier stromaufwärts vom angestau¬ ten Turbinenventil 31. Sobald der Drucksollwert 41 unter- be¬ ziehungsweise überschritten wird, erfolgt das Öffnen bezie¬ hungsweise Schließen der Zuführungen 71 und 81 über entspre- chende Ansteuerungen 72 und 82, so dass ein veränderter Wasseranteil den Einspritzkühlungen 73 und 83 zugeführt wird. Dieser variable Wasseranteil wird solange in den Dampfmassen¬ strom eingebracht, bis ein angepasster Dampftemperatursoll¬ wert 49 erreicht ist. Dieser bestimmt sich im vorliegenden Beispiel aus der Differenz eines vorgegebenen Dampftempera- turgrundsollwertes 45 und dem Ausgangswert eines proportio¬ nal-integral (PI-) wirkenden Reglers 48, der die Differenz aus Druckmessung 32 und Drucksollwert 41 auswertet und aus¬ gleicht. In der anschließenden Regeleinrichtung 100 wird die- ser zeitlich variable Dampftemperatursollwert 49 als verän¬ derliche Eingangsgröße für die Dampftemperaturregelungsein- richtung 100 vorgegeben und verwendet. Anstelle des PI- Reglers 48 könnte genauso ein einfacher P-Regler oder auch ein PID-Regler oder auch ein anderer, gleichwertig wirkender Regler zum Einsatz kommen, wobei sich im vorliegenden Beispiel der PI-Regler als vorteilhaft erwiesen hat. The operation is controlled by the turbine valve 31 of the medium-pressure stage 2. For this purpose, the rotor via a Messeinrich ¬ device 21, the current output of the steam turbine and with ermit ¬ telt an associated power set point, always adjust itself depending on the required primary control reserve as ¬ the can, compared. In the case of a difference between two values - which corresponds to a "required power change." - then targeted ANPAS ¬ solution of the opening position of the turbine valve 31 takes place in such a way that at the end desired and actual values are identical again, the pressure is controlled substantially by changed insertion of a variable proportion of water in the steam mass flow for the high pressure stage 1 by means of injection cooling 73, which is advantageously used as Zwischeneinspritz- high pressure device shown of a here not further superheater realized. Optional here comple ¬ zend an additional modified introduction of a variable proportion of water in the Steam mass flow for the Mitteldruckstu ¬ Fe 2 is provided by means of the injection cooling 83, which is also advantageously realized as an intermediate injection device of a reheater not shown here in detail rt 41 compared with a pressure measurement 32 of the steam mass flow. The pressure measurement 32 is performed here upstream of the attached jam ¬ th turbine valve 31 as soon as the desired pressure value is exceeded 41 under- be ¬ relationship instance, the opening takes place rela ¬ hung as closing the inlets 71 and 81 via corresponding control systems 72 and 82, so that a modified Water content is supplied to the injection cooling 73 and 83. This variable proportion of water is introduced into the steam mass stream until an adjusted steam temperature setpoint value 49 is reached. This is determined in the present example the difference between a predetermined Dampftempera- turgrundsollwertes 45 and acting the output of a proportio nal ¬-integral (PI) controller 48 which evaluates the difference between the pressure measurement 32 and pressure setpoint 41 and compensates for ¬. In the subsequent control device 100 is DIE ser temporally variable steam temperature set value 49 determined as changed ¬ derliche input variable for the Dampftemperaturregelungsein- device 100 and used. Instead of the PI controller 48 could just as a simple P-controller or a PID controller or other, equivalent acting regulator can be used, in the present example, the PI controller has proved advantageous.

Claims

Patentansprüche claims
1. Verfahren zur kurzfristigen Leistungsanpassung einer 1. Short-term performance adjustment procedure
Dampfturbine eines Gas- und Dampfkraftwerks für die Primärre- gelung, umfassend die Schritte: Steam turbine of a gas and steam power plant for the primary control, comprising the steps:
- Öffnen beziehungsweise Schließen eines angestauten Turbinenventils (31, 51), zumindest einer Druckstufe (1, 2, 3, 4) der Dampfturbine, in Abhängigkeit von einer geforderten Leistungsänderung,  Opening or closing a pent-up turbine valve (31, 51), at least one pressure stage (1, 2, 3, 4) of the steam turbine, as a function of a demanded power change,
- Vergleich eines vorgegebenen Drucksollwerts (41) mit einer Druckmessung (32), die stromaufwärts vom angestauten Turbinenventil (31, 51) den Druck des in die zumindest eine Druckstufe (1, 2, 3, 4) einströmenden Dampfmassenstroms misst , Comparing a predetermined pressure setpoint (41) with a pressure measurement (32) measuring upstream of the accumulated turbine valve (31, 51) the pressure of the steam mass flow flowing into the at least one pressure stage (1, 2, 3, 4),
- Öffnen beziehungsweise Schließen einer Zuführung (71, 81) zum Einbringen eines variablen Wasseranteils in den Dampfmassenstrom zumindest einer der Druckstufen (1, 2, 3, 4) sobald der Drucksollwert (41) unter- beziehungsweise über¬ schritten wird, - opening or closing a feed (71, 81) for introducing a variable proportion of water in the steam mass flow, at least one of the pressure stages (1, 2, 3, 4) as soon as the pressure setpoint (41) lower or steps over ¬ is
- wobei der variable Wasseranteil solange in den Dampfmassen¬ strom eingebracht wird, bis ein angepasster Dampftempera- tursollwert (49) erreicht ist, welcher sich aus der Diffe¬ renz eines vorgegebenen Dampftemperaturgrundsollwertes (45) und dem Ausgangswert eines zumindest proportional wirkenden Reglers (48), der die Differenz aus Druckmessung (32) und- wherein the variable water content is as long as introduced into the steam mass ¬ stream, to an adjusted Dampftempera- temperature setpoint (49) is reached, which is comprised of the Diffe ¬ ence of a predetermined vapor temperature basic target value (45) and the output value of an at least proportionally acting controller (48) taking the difference from pressure measurement (32) and
Drucksollwert (41) auswertet und ausgleicht, bestimmt. Pressure setpoint (41) evaluates and compensates, determined.
2. Verfahren nach Anspruch 1, 2. The method according to claim 1,
d a d u r c h g e k e n n z e i c h n e t , d a s s d a d u r c h e s e n c i n e s, d a s s
die Einbringung eines variablen Wasseranteils in den Dampfmassenstrom mittels einer Einspritzkühlung (73, 83) erfolgt. the introduction of a variable proportion of water in the steam mass flow by means of an injection cooling (73, 83) takes place.
3. Verfahren nach Anspruch 1, 3. The method according to claim 1,
d a d u r c h g e k e n n z e i c h n e t , d a s s d a d u r c h e s e n c i n e s, d a s s
die Einbringung eines variablen Wasseranteils in den Dampfmassenstrom mittels einer Veränderung des in einen der Dampfturbine vorgeschalteten Dampferzeugers einströmenden Speise- wassermassenstroms erfolgt. the introduction of a variable proportion of water into the steam mass flow by means of a change in the feedstock flowing into a steam generator upstream of the steam turbine. water mass flow takes place.
4. Verfahren nach einem der Ansprüche 1 bis 3, 4. The method according to any one of claims 1 to 3,
d a d u r c h g e k e n n z e i c h n e t , d a s s das Öffnen beziehungsweise Schließen am Turbinenventil (31) der Mitteldruckstufe (2) der Dampfturbine erfolgt. That is, the opening or closing on the turbine valve (31) of the medium-pressure stage (2) of the steam turbine takes place.
5. Verfahren nach Anspruch 4, 5. The method according to claim 4,
d a d u r c h g e k e n n z e i c h n e t , d a s s das Zuführen eines variablen Wasseranteils in den, in died a d u r c h e c e n e s, the feeding of a variable proportion of water into the, into the
Hochdruckstufe (1) der Dampfturbine, einströmenden Dampfmas¬ senstrom erfolgt. High pressure stage (1) of the steam turbine, incoming Dampfmas ¬ senstrom takes place.
6. Verfahren nach einem der Ansprüche 1 bis 5, 6. The method according to any one of claims 1 to 5,
d a d u r c h g e k e n n z e i c h n e t , d a s s das Einbringen eines variablen Wasseranteils und das Öffnen beziehungsweise Schließen am Turbinenventil in mehreren der Druckstufen (1, 2, 3, 4) der Dampfturbine erfolgt. That is, the introduction of a variable proportion of water and the opening or closing of the turbine valve in several of the pressure stages (1, 2, 3, 4) of the steam turbine takes place.
EP17780006.7A 2016-09-28 2017-08-24 Method for the short-term adjustment of the output of a combined-cycle power plant steam turbine, for primary frequency control Withdrawn EP3475539A1 (en)

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