EP2611995B1 - Steam turbine plant with variable steam supply - Google Patents

Steam turbine plant with variable steam supply Download PDF

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Publication number
EP2611995B1
EP2611995B1 EP11771088.9A EP11771088A EP2611995B1 EP 2611995 B1 EP2611995 B1 EP 2611995B1 EP 11771088 A EP11771088 A EP 11771088A EP 2611995 B1 EP2611995 B1 EP 2611995B1
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EP
European Patent Office
Prior art keywords
steam
pressure
feed
inlet
turbine
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.)
Not-in-force
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EP11771088.9A
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German (de)
French (fr)
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EP2611995A1 (en
Inventor
Norbert Pieper
Michael Wechsung
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Siemens AG
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Siemens AG
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Publication of EP2611995A1 publication Critical patent/EP2611995A1/en
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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
    • 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
    • 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
    • F01K23/106—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 with water evaporated or preheated at different pressures in exhaust boiler
    • F01K23/108—Regulating means specially adapted therefor
    • 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
    • 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
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines

Definitions

  • the invention relates to a steam turbine plant with variable steam feed.
  • Steam turbine plants are usually dimensioned from an economic point of view.
  • steam turbine plants which are used in electrical energy production, is worked to achieve maximum efficiency with very large power units.
  • the efficiency should also be constant over the largest possible power range.
  • it is known to feed a Zudampf, in particular a low-pressure Zudampf, in a medium or low-pressure steam turbine. If the steam turbine is driven, for example, in part-load operation, the Zudampf must be throttled at the feed point, if this is available at constant pressure.
  • WO-A1-2011 / 030285 is a steam turbine plant known with a high pressure, medium pressure and low pressure turbine.
  • the medium-pressure and low-pressure turbines each have a diverting station to be able to vary the amount of steam above the respective turbines.
  • From the DE 102 27 709 A1 is a steam turbine plant with one between high-pressure turbine and medium-pressure or low-pressure turbine arranged reheater known.
  • a check valve is arranged between high-pressure turbine outlet and reheater inlet.
  • a safe and fast startup from the cold state or a load shutdown is made possible by the fact that further provided an overflow, which, bridging the reheater connects the high-pressure exhaust steam line of the high-pressure turbine with the medium-pressure turbine.
  • From the JP 60 166 704 A a steam turbine with a condenser is known in which a circuit is provided to leave the condenser after the shutdown of the steam turbine at low pressure.
  • a control unit is provided, the valves accordingly sets and closes.
  • the invention has for its object to provide a steam turbine plant, in which the above problems are overcome and in particular throttle losses are largely avoided. It is another object of the invention to propose a method for operating the steam turbine plant, in which throttle losses are largely avoided.
  • the Zudampfsammel Arthur is introduced at a Zudampfeinleitstelle the Zudampf effetsabitess in the exhaust steam of the steam turbine and a feed steam device is provided on the steam turbine with a changeover, with the upstream of the Zudampfeinleitstelle the feed steam device is connected to the Zudampf niesabêt and which is switchable such that when the Abdampf réelle is less than a target pressure in the Zudampf niesabterrorism, the Zudampf endeavorsabterrorism is vapor-connected to the feed steam device and is interrupted between the changeover valve and the Zudampfeinleitstelle, and otherwise the feed steam device from the Zudampf effetsabexcellent is disconnected.
  • the changeover valve is switched in the Zudampf founded founded upon by a feed steam via the feed steam device. If the exhaust steam pressure of the steam turbine is equal to or greater than the target value, the feed steam device is separated from the steam exhaust line section and the steam turbine receives no feed steam via the feed steam device.
  • the Zudampf can be introduced via the feed steam device upstream and relaxed in the steam turbine means of Umschaltarmatur.
  • the feed steam device preferably has a plurality of steam feed points at different stages of the steam turbine and the feed steam device can be controlled such that the feed steam is fed in only at that steam feed point at which the pressure at the introduction position within the steam turbine is higher than that of the feed steam itself However, the pressure difference is minimal.
  • the feed steam is thus fed into the steam turbine such that any necessary throttling of the feed steam is dispensable, whereby the steam turbine plant according to the invention is free from unnecessary throttling losses.
  • the feed steam device is preferably controlled such that, starting from the Dampfeinspeisestelle which is formed on a steam side arranged stage of the steam turbine, the feed steam device controls that Dampfeinspeisestelle formed at an adjacent, upstream stage of the steam turbine.
  • the feed steam device is thus formed in this embodiment, to redirect at load reduction of the medium-pressure steam turbine from the controlled at one stage of the medium-pressure steam turbine steam feed to an adjacent, upstream steam feed.
  • the feed steam device is controlled with load increase of the steam turbine such that, starting from a steam feed, which is formed at an upstream stage of the steam turbine, the feed steam device that steam feed point controls, which is formed on an adjacent, steam side arranged stage of the steam turbine.
  • a medium or low pressure steam turbine is preferably provided as a steam consumer of the steam turbine plant.
  • the feed steam device is designed to control the increase in load of the medium-pressure steam turbine from the steam feed point controlled at one stage of the medium-pressure steam turbine to an adjacent, steam feed point arranged downstream.
  • the opening degree characteristic of the switching valve for connecting and disconnecting the feed steam device and / or the opening degree characteristic for connecting and disconnecting the steam pipe section are preferably linear, progressive or degressive.
  • a method for operating the steam turbine plant preferably has the steps of: providing the steam turbine plant; Setting a target pressure for the steam manifold; Switching the changeover valve so that when the exhaust pressure is lower than the target pressure in the Zudampf niesabites, the Zudampf effetsabites is vapor-connected to the feed steam device and is interrupted between the changeover valve and the Zudampfeinleitstelle; or switching the changeover valve so that when the exhaust steam pressure is equal to or higher than the target pressure in the Zudampf niesabterrorism, the feed steam device is separated from the changeover valve and is conveyed to the Zudampfeinleitstelle Zudampf directly from the Zudampf effet effet.
  • the feed steam device preferably has a plurality of steam feed points at different stages of the steam turbine and the feed steam device is controlled such that the feed steam is fed only at the steam feed point at which the pressure difference between the feed position within the steam turbine and the feed steam is minimal is.
  • the feed steam device is preferably controlled such that, starting from the Dampfeinspeisestelle which is formed on a steam side arranged stage of the steam turbine, the feed steam device controls that Dampfeinspeisestelle formed at an adjacent, upstream stage of the steam turbine.
  • the feed steam device When load of the steam turbine, the feed steam device is preferably controlled such that, starting from a steam feed, which is formed at an upstream stage of the steam turbine, the feed steam device controls that steam feed, which is formed on an adjacent, steam side arranged stage of the steam turbine.
  • a steam turbine plant 1 is shown, which is coupled via a waste heat boiler 2 with a gas turbine plant 3.
  • the waste heat boiler 2 comprises a high pressure steam system 4 with a live steam manifold 14, a medium pressure steam system 5 with a medium pressure steam manifold 15, a low pressure steam system 6 with a low pressure steam manifold 16 and a plurality of heat exchangers 7.
  • the heat energy of the hot exhaust gases of the gas turbine plant 3 is discharged by means of the heat exchanger 7 to a respective associated boiler system 8, 9 and 10 for generating steam.
  • the steam generated in the boiler systems 8, 9 and 10 is used to operate a high pressure steam turbine 11, a medium pressure steam turbine 12 and a low pressure steam turbine 13.
  • the high-pressure steam turbine 11 and the medium-pressure steam turbine 12 are each coupled by means of one of the steam manifolds 14 and 15 with the respectively corresponding steam system 4 and 5 respectively.
  • the medium-pressure Zudampfsammeltechnisch 15 further includes a reheater 20, by means of which a medium-pressure steam to increase the efficiency of the steam turbine plant 1 in the waste heat boiler 2 is overheated.
  • the medium-pressure steam is composed of the medium-pressure Zudampf generated in the boiler system 9 and the exhaust steam of the high-pressure steam turbine 11. From the reheater 20, the superheated medium-pressure steam flows via the medium-pressure steam manifold 22 to the medium-pressure steam turbine 12th
  • the low-pressure Zudampf flows from the boiler system 10 to a changeover valve 17.
  • the pressure of Zudampfs in the low-pressure Zudampfsammeltechnisch 16 is presently 4.2 bar.
  • the pressure of the low-pressure Zudampfs is increased such that condensation of sulfurous acid on the heat transfer surfaces of the heat exchanger 7 and thus corroding the heat exchanger surfaces is prevented. This results in the low-pressure steam manifold 16, a pressure of, for example, 8 bar.
  • the low-pressure steam collecting line 16 also has a low-pressure Zudampf niethylcholine 19, on which a Zudampfeinleitstelle 21 is formed. Via the Zudampfeinleitstelle 21 of the low-pressure Zudampf is fed via the low-pressure Zudampf effetsabites 19 with the exhaust steam of the medium-pressure turbine 12.
  • the reversing valve 17 is associated with a control device (not shown) which is set to switch the change-over valve 17 in such a way when the exhaust pressure of the medium-pressure steam turbine 12 falls below a predetermined desired value, for example 4 bar, caused in particular by a partial load operation of the medium-pressure steam turbine 12 in that the exhaust steam flows via the changeover valve 17 to a feed steam device 18. If, for example, the operating state of the medium-pressure steam turbine 12 drops from a full-load operation to a partial-load operation of 60% of the full load, the exhaust-steam pressure also drops accordingly, ie the exhaust-steam pressure drops to 60% of the exhaust-steam pressure at full load.
  • a control device not shown
  • the desired value is undershot and the change-over valve 17 is switched, whereby the spent steam flows to the feed steam device 18, via which it flows as feed steam into the medium-pressure turbine 12.
  • the Zudampf from the pressure level in the low-pressure Zudampfsammeltechnisch 16 is relaxed to the pressure level at the Zudampfeinleitstelle 21 in the medium-pressure turbine 12 and thus energetically utilized.
  • the feed steam device 18 has a plurality of steam feed points (not shown), of which only a maximum of one is activated. That is, the steam is always supplied only at a Dampfeinspeisestelle. In this case, that steam feed point is controlled, at which the pressure of the steam turbine process steam is approximately equal to the pressure of the feed steam. This allows almost unthrottled feeding the feed steam, whereby an additional throttle loss is avoided by throttling. Due to flow losses, the Zudampf after passing the changeover valve 17 at the Dampfeinspeisestelle a slightly lower pressure than in the low pressure Zudampfsammeltechnisch 16, for example, 4 bar.
  • the changeover valve 17 is switched such that the exhaust steam flow flows via the low-pressure Zudampf Obersabites 19 to the low-pressure steam turbine 13.
  • the low-pressure Zudampf nieitstelle 21 of the exhaust steam of the medium-pressure turbine 12 which was previously relaxed to 4 bar
  • the steam of the low pressure Zudampfsammeltechnisch 16 which in this case also has a pressure of 4 bar together and to the low-pressure turbine thirteenth ,

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Description

Die Erfindung betrifft eine Dampfturbinenanlage mit variabler Dampfeinspeisung.The invention relates to a steam turbine plant with variable steam feed.

Dampfturbinenanlagen werden in der Regel unter ökonomischen Gesichtspunkten dimensioniert. Insbesondere bei Dampfturbinenanlagen, die in der elektrischen Energieerzeugung eingesetzt werden, wird zum Erreichen höchster Wirkungsgrade mit sehr großen Leistungseinheiten gearbeitet. Der Wirkungsgrad soll zudem über einen möglichst großen Leistungsbereich konstant sein. Dazu ist es bekannt einen Zudampf, insbesondere einen Niederdruck-Zudampf, in eine Mittel- oder NiederdruckDampfturbine einzuspeisen. Wird die Dampfturbine beispielsweise im Teillastbetrieb gefahren, muss der Zudampf an der Einspeisestelle angedrosselt werden, sofern dieser bei konstantem Druck zur Verfügung steht.Steam turbine plants are usually dimensioned from an economic point of view. In particular, in steam turbine plants, which are used in electrical energy production, is worked to achieve maximum efficiency with very large power units. The efficiency should also be constant over the largest possible power range. For this purpose, it is known to feed a Zudampf, in particular a low-pressure Zudampf, in a medium or low-pressure steam turbine. If the steam turbine is driven, for example, in part-load operation, the Zudampf must be throttled at the feed point, if this is available at constant pressure.

In kombinierten Gas- und Dampfturbinenanlagen wird Dampf auf mehreren Druckstufen erzeugt, beispielsweise Frischdampf, Mitteldruck-Zudampf und Niederdruck-Zudampf beim Drei-Druck-Prozess. Häufig wird dabei ein Brennstoff mit einem hohen Schwefelgehalt verwendet. Dabei kann es notwendig sein, den Druck des Niederdruck-Zudampfs zu erhöhen, um ein Auskondensieren von schwefliger Säure an den Wärmeübertragerflächen eines Dampferzeugers aufgrund des hohen Schwefelgehalts des Brennstoffs zu verhindern. Im Gegenzug muss der Niederdruck-Zudampf entsprechend an der Einspeisestelle angedrosselt werden. Nachteilig dabei ist, dass mit dem Androsseln des Zudampfs Energie vernichtet wird, also die Fähigkeit des Dampfs abnimmt im Kreisprozess Arbeit zu verrichten, wodurch der Wirkungsgrad des gesamten Dampfkraftprozesses sinkt.In combined gas and steam turbine plants, steam is generated at several pressure stages, for example live steam, medium pressure steam and low pressure steam in the three-pressure process. Frequently, a fuel with a high sulfur content is used. It may be necessary to increase the pressure of the low pressure Zudampfs to prevent condensation of sulfurous acid on the heat exchanger surfaces of a steam generator due to the high sulfur content of the fuel. In return, the low-pressure Zudampf must be throttled accordingly at the feed point. The disadvantage here is that with the throttling of the Zudampfs energy is destroyed, so the ability of the steam decreases in the cycle process to perform work, whereby the efficiency of the entire steam power process decreases.

Aus der WO-A1-2011/030285 ist eine Dampfturbinenanlage bekannt mit einer Hochdruck-, Mitteldruck- und Niederdruck-Turbine. Die Mitteldruck- und Niederdruck-Turbinen haben jeweils eine Umleitstation um die Dampfmenge über den jeweiligen Turbinen variieren zu können.From the WO-A1-2011 / 030285 is a steam turbine plant known with a high pressure, medium pressure and low pressure turbine. The medium-pressure and low-pressure turbines each have a diverting station to be able to vary the amount of steam above the respective turbines.

Aus der DE 102 27 709 A1 ist eine Dampfturbinenanlage mit einem zwischen Hochdruckturbine und Mitteldruck- oder Niederdruckturbine angeordneten Zwischenüberhitzer bekannt. Dabei ist zwischen Hochdruckturbinenaustritt und Zwischenüberhitzereintritt ein Rückschlagventil angeordnet. Ein sicheres und schnelles Hochfahren aus dem kalten Zustand respektive eine Lastabschaltung wird dadurch ermöglicht, dass weiterhin eine Überströmleitung vorgesehen ist, welche, den Zwischenüberhitzer überbrückend, die Hochdruck-Abdampfleitung der Hochdruckturbine mit der Mitteldruckturbine verbindet. Aus der JP 60 166 704 A ist eine Dampfturbine mit einem Kondensator bekannt, bei der eine Schaltung vorhanden ist, den Kondensator nach dem Abfahren der Dampfturbine auf niedrigem Druck zu belassen. Dazu ist ein Steuergerät vorhanden, das Ventile entsprechend setuert un schließt. Es ist eine zum Kondensator führende Dampfsammelleitung vorhanden.From the DE 102 27 709 A1 is a steam turbine plant with one between high-pressure turbine and medium-pressure or low-pressure turbine arranged reheater known. In this case, a check valve is arranged between high-pressure turbine outlet and reheater inlet. A safe and fast startup from the cold state or a load shutdown is made possible by the fact that further provided an overflow, which, bridging the reheater connects the high-pressure exhaust steam line of the high-pressure turbine with the medium-pressure turbine. From the JP 60 166 704 A a steam turbine with a condenser is known in which a circuit is provided to leave the condenser after the shutdown of the steam turbine at low pressure. For this purpose, a control unit is provided, the valves accordingly sets and closes. There is a steam manifold leading to the condenser.

Der Erfindung liegt die Aufgabe zugrunde, eine Dampfturbinenanlage zu schaffen, bei der die oben genannten Probleme überwunden sind und insbesondere Drosselverluste weitestgehend vermieden sind. Ferner ist es Aufgabe der Erfindung ein Verfahren zum Betreiben der Dampfturbinenanlage vorzuschlagen, bei dem insbesondere Drosselverluste weitestgehend vermieden werden.The invention has for its object to provide a steam turbine plant, in which the above problems are overcome and in particular throttle losses are largely avoided. It is another object of the invention to propose a method for operating the steam turbine plant, in which throttle losses are largely avoided.

Die Aufgabe ist erfindungsgemäß mit einer Dampfturbinenanlage gemäß Anspruch 1 gelöst. Ferner ist die Aufgabe mit einem Verfahren gemäß Anspruch 6 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den abhängigen Ansprüchen beschrieben.The object is achieved according to the invention with a steam turbine plant according to claim 1. Furthermore, the object is achieved by a method according to claim 6. Advantageous developments of the invention are described in the dependent claims.

Bei einer Dampfturbinenanlage mit einer Dampfturbine und einer einen Zudampfleitungsabschnitt aufweisenden Zudampfsammelleitung zur Versorgung eines Dampfverbrauchers ist die Zudampfsammelleitung an einer Zudampfeinleitstelle des Zudampfleitungsabschnitts in den Abdampfstrom der Dampfturbine eingeleitet und eine Einspeisedampfvorrichtung ist an der Dampfturbine mit einer Umschaltarmatur vorgesehen, mit der stromauf der Zudampfeinleitstelle die Einspeisedampfvorrichtung an den Zudampfleitungsabschnitt angeschlossen ist und die derart umschaltbar ist, dass, wenn der Abdampfdruck kleiner einem Soll-Druck in dem Zudampfleitungsabschnitt ist, der Zudampfleitungsabschnitt mit der Einspeisedampfvorrichtung dampfleitend verbunden und zwischen der Umschaltarmatur und der Zudampfeinleitstelle unterbrochen ist, sowie sonst die Einspeisedampfvorrichtung von dem Zudampfleitungsabschnitt getrennt ist.In a steam turbine plant with a steam turbine and a Zudampfleitungsabschnitt having Zudampfsammelleitung for supplying a steam consumer, the Zudampfsammelleitung is introduced at a Zudampfeinleitstelle the Zudampfleitungsabschnitts in the exhaust steam of the steam turbine and a feed steam device is provided on the steam turbine with a changeover, with the upstream of the Zudampfeinleitstelle the feed steam device is connected to the Zudampfleitungsabschnitt and which is switchable such that when the Abdampfdruck is less than a target pressure in the Zudampfleitungsabschnitt, the Zudampfleitungsabschnitt is vapor-connected to the feed steam device and is interrupted between the changeover valve and the Zudampfeinleitstelle, and otherwise the feed steam device from the Zudampfleitungsabschnitt is disconnected.

Erfindungsgemäß wird die Umschaltarmatur bei einem Unterschreiten des Soll-Drucks in dem Zudampfleitungsabschnitt derart geschaltet, dass die Dampfturbine mit einem Einspeisedampf via die Einspeisedampfvorrichtung beaufschlagt wird. Entspricht der Abdampfdruck der Dampfturbine dem Soll-Wert, oder liegt er darüber, ist die Einspeisedampfvorrichtung von dem Zudampfleitungsabschnitt getrennt und die Dampfturbine erhält keinen Einspeisedampf via die Einspeisedampfvorrichtung. Wird die Dampfturbinenanlage in Teillast betrieben, wodurch der Druck im Dampfturbineninneren entsprechend abfällt, oder wird ein stark schwefelhaltiger Brennstoff beim Betrieb einer an die Dampfturbinenanlage gekoppelten Gasturbinenanlage verwendet, wobei der Niederdruckdampfdruck in der Regel erhöht wird, um ein Auskondensieren von schwefliger Säure und somit ein Korrodieren von Bauteilen des Abhitzekessels zu verhindern, kann mittels der Umschaltarmatur der Zudampf über die Einspeisedampfvorrichtung stromauf eingeleitet und in der Dampfturbine entspannt werden.According to the invention, the changeover valve is switched in the Zudampfleitungsabschnitt when falling below the target pressure in such a way that the steam turbine is acted upon by a feed steam via the feed steam device. If the exhaust steam pressure of the steam turbine is equal to or greater than the target value, the feed steam device is separated from the steam exhaust line section and the steam turbine receives no feed steam via the feed steam device. If the steam turbine plant is operated at partial load, whereby the pressure in the steam turbine interior drops accordingly, or a highly sulfur-containing fuel is used in the operation of coupled to the steam turbine plant gas turbine plant, wherein the low-pressure vapor pressure is usually increased, to condense out sulfurous acid and thus corrosion To prevent components of the waste heat boiler, the Zudampf can be introduced via the feed steam device upstream and relaxed in the steam turbine means of Umschaltarmatur.

Die Einspeisedampfvorrichtung weist bevorzugt eine Mehrzahl an Dampfeinspeisestellen an unterschiedlichen Stufen der Dampfturbine auf und die Einspeisedampfvorrichtung ist derart ansteuerbar, dass die Einspeisung des Einspeisedampfes nur an derjenigen Dampfeinspeisestelle erfolgt, an der der Druck an der Einleitposition innerhalb der Dampfturbine zwar höher ist als der des Einspeisedampfs selbst, die Druckdifferenz jedoch minimal ist. Der Einspeisedampf wird folglich derart in die Dampfturbine eingespeist, dass eine gegebenenfalls erforderliche Drosselung des Einspeisedampfs entbehrlich ist, wodurch die erfindungsgemäße Dampfturbinenanlage frei von unnötigen Drosselverlusten ist.The feed steam device preferably has a plurality of steam feed points at different stages of the steam turbine and the feed steam device can be controlled such that the feed steam is fed in only at that steam feed point at which the pressure at the introduction position within the steam turbine is higher than that of the feed steam itself However, the pressure difference is minimal. The feed steam is thus fed into the steam turbine such that any necessary throttling of the feed steam is dispensable, whereby the steam turbine plant according to the invention is free from unnecessary throttling losses.

Bei Lastabsenkung der Dampfturbine ist die Einspeisedampfvorrichtung bevorzugt derart angesteuert, dass ausgehend von der Dampfeinspeisestelle, die an einer abdampfseitig angeordneten Stufe der Dampfturbine ausgebildet ist, die Einspeisedampfvorrichtung diejenige Dampfeinspeisestelle ansteuert, die an einer angrenzenden, stromauf angeordneten Stufe der Dampfturbine ausgebildet ist.When load reduction of the steam turbine, the feed steam device is preferably controlled such that, starting from the Dampfeinspeisestelle which is formed on a steam side arranged stage of the steam turbine, the feed steam device controls that Dampfeinspeisestelle formed at an adjacent, upstream stage of the steam turbine.

Die Einspeisedampfvorrichtung ist bei dieser Ausführungsform also ausgebildet, bei Lastabsenkung der Mitteldruckdampfturbine von der an einer Stufe der Mitteldruckdampfturbine angesteuerten Dampfeinspeisestelle auf eine angrenzende, stromauf angeordnete Dampfeinspeisestelle umzusteuern.The feed steam device is thus formed in this embodiment, to redirect at load reduction of the medium-pressure steam turbine from the controlled at one stage of the medium-pressure steam turbine steam feed to an adjacent, upstream steam feed.

Bevorzugtermaßen ist die Einspeisedampfvorrichtung bei Lastzunahme der Dampfturbine derart angesteuert, dass ausgehend von einer Dampfeinspeisestelle, die an einer stromauf angeordneten Stufe der Dampfturbine ausgebildet ist, die Einspeisedampfvorrichtung diejenige Dampfeinspeisestelle ansteuert, die an einer angrenzenden, abdampfseitig angeordneten Stufe der Dampfturbine ausgebildet ist. Als Dampfverbraucher der Dampfturbinenanlage ist bevorzugt eine Mittel- oder Niederdruckdampfturbine vorgesehen.Preferably, the feed steam device is controlled with load increase of the steam turbine such that, starting from a steam feed, which is formed at an upstream stage of the steam turbine, the feed steam device that steam feed point controls, which is formed on an adjacent, steam side arranged stage of the steam turbine. As a steam consumer of the steam turbine plant, a medium or low pressure steam turbine is preferably provided.

Die Einspeisedampfvorrichtung ist bei dieser Ausführungsform also ausgebildet, bei Lasterhöhung der Mitteldruckdampfturbine von der an einer Stufe der Mitteldruckdampfturbine angesteuerten Dampfeinspeisestelle auf eine angrenzende, stromab angeordnete Dampfeinspeisestelle umzusteuern.In this embodiment, therefore, the feed steam device is designed to control the increase in load of the medium-pressure steam turbine from the steam feed point controlled at one stage of the medium-pressure steam turbine to an adjacent, steam feed point arranged downstream.

Ferner sind bevorzugt die Öffnungsgradkennlinie der Umschaltarmatur für das Verbinden und Trennen der Einspeisedampfvorrichtung und/oder die Öffnungsgradkennlinie für das Verbinden und Trennen des Zudampfleitungsabschnitts linear, progressiv oder degressiv.Further, the opening degree characteristic of the switching valve for connecting and disconnecting the feed steam device and / or the opening degree characteristic for connecting and disconnecting the steam pipe section are preferably linear, progressive or degressive.

Ein Verfahren zum Betreiben der Dampfturbinenanlage weist bevorzugt die Schritte auf: Bereitstellen der Dampfturbinenanlage; Festlegen eines Soll-Drucks für die Zudampfsammelleitung; Schalten der Umschaltarmatur so, dass, wenn der Abdampfdruck kleiner dem Soll-Druck in dem Zudampfleitungsabschnitt ist, der Zudampfleitungsabschnitt mit der Einspeisedampfvorrichtung dampfleitend verbunden und zwischen der Umschaltarmatur und der Zudampfeinleitstelle unterbrochen ist; oder Schalten der Umschaltarmatur so, dass, wenn der Abdampfdruck gleich oder größer dem Soll-Druck in dem Zudampfleitungsabschnitt ist, die Einspeisedampfvorrichtung von der Umschaltarmatur getrennt und an die Zudampfeinleitstelle Zudampf direkt von dem Zudampfleitungsabschnitt gefördert wird.A method for operating the steam turbine plant preferably has the steps of: providing the steam turbine plant; Setting a target pressure for the steam manifold; Switching the changeover valve so that when the exhaust pressure is lower than the target pressure in the Zudampfleitungsabschnitt, the Zudampfleitungsabschnitt is vapor-connected to the feed steam device and is interrupted between the changeover valve and the Zudampfeinleitstelle; or switching the changeover valve so that when the exhaust steam pressure is equal to or higher than the target pressure in the Zudampfleitungsabschnitt, the feed steam device is separated from the changeover valve and is conveyed to the Zudampfeinleitstelle Zudampf directly from the Zudampfleitungsabschnitt.

Bei dem Verfahren weist ferner bevorzugt die Einspeisedampfvorrichtung eine Mehrzahl an Dampfeinspeisestellen an unterschiedlichen Stufen der Dampfturbine auf und die Einspeisedampfvorrichtung wird derart angesteuert, dass die Einspeisung des Einspeisedampfes nur an derjenigen Dampfeinspeisestelle erfolgt, an der die Druckdifferenz zwischen der Einspeiseposition innerhalb der Dampfturbine und dem Einspeisedampf minimal ist. Dabei wird bei Lastabsenkung der Dampfturbine die Einspeisedampfvorrichtung bevorzugt derart angesteuert, dass ausgehend von der Dampfeinspeisestelle, die an einer abdampfseitig angeordneten Stufe der Dampfturbine ausgebildet ist, die Einspeisedampfvorrichtung diejenige Dampfeinspeisestelle ansteuert, die an einer angrenzenden, stromauf angeordneten Stufe der Dampfturbine ausgebildet ist. Bei Lastzunahme der Dampfturbine wird die Einspeisedampfvorrichtung bevorzugt derart angesteuert, dass ausgehend von einer Dampfeinspeisestelle, die an einer stromauf angeordneten Stufe der Dampfturbine ausgebildet ist, die Einspeisedampfvorrichtung diejenige Dampfeinspeisestelle ansteuert, die an einer angrenzenden, abdampfseitig angeordneten Stufe der Dampfturbine ausgebildet ist.In the method, furthermore, the feed steam device preferably has a plurality of steam feed points at different stages of the steam turbine and the feed steam device is controlled such that the feed steam is fed only at the steam feed point at which the pressure difference between the feed position within the steam turbine and the feed steam is minimal is. In this case, when load reduction of the steam turbine, the feed steam device is preferably controlled such that, starting from the Dampfeinspeisestelle which is formed on a steam side arranged stage of the steam turbine, the feed steam device controls that Dampfeinspeisestelle formed at an adjacent, upstream stage of the steam turbine. When load of the steam turbine, the feed steam device is preferably controlled such that, starting from a steam feed, which is formed at an upstream stage of the steam turbine, the feed steam device controls that steam feed, which is formed on an adjacent, steam side arranged stage of the steam turbine.

Im Folgenden wird eine bevorzugte Ausführungsform einer erfindungsgemäßen Gas- und Dampfturbinenanlage anhand der beigefügten schematischen Zeichnung erläutert. Es zeigt die Figur eine Gas- und Dampfturbinenanlage mit variabler Dampfeinspeisung.In the following, a preferred embodiment of a gas and steam turbine plant according to the invention will be explained with reference to the accompanying schematic drawing. It shows the figure of a gas and steam turbine plant with variable steam feed.

In der Figur ist eine Dampfturbinenanlage 1 gezeigt, die via einen Abhitzekessel 2 mit einer Gasturbinenanlage 3 gekoppelt ist. Der Abhitzekessel 2 umfasst ein Hochdruckdampfsystem 4 mit einer Frischdampfsammelleitung 14, ein Mitteldruckdampfsystem 5 mit einer Mitteldruck-Zudampfsammelleitung 15, ein Niederdruckdampfsystem 6 mit einer Niederdruck-Zudampfsammelleitung 16 sowie mehrere Wärmeübertrager 7.In the figure, a steam turbine plant 1 is shown, which is coupled via a waste heat boiler 2 with a gas turbine plant 3. The waste heat boiler 2 comprises a high pressure steam system 4 with a live steam manifold 14, a medium pressure steam system 5 with a medium pressure steam manifold 15, a low pressure steam system 6 with a low pressure steam manifold 16 and a plurality of heat exchangers 7.

In dem Abhitzekessel 2 wird die Wärmeenergie der heißen Abgase der Gasturbinenanlage 3 mittels der Wärmeübertrager 7 an eine jeweils zugehörige Kesselanlage 8, 9 und 10 zum Erzeugen von Dampf abgegeben. Der in den Kesselanlagen 8, 9 und 10 erzeugte Dampf dient zum Betreiben einer Hochdruckdampfturbine 11, einer Mitteldruckdampfturbine 12 und einer Niederdruckdampfturbine 13.In the waste heat boiler 2, the heat energy of the hot exhaust gases of the gas turbine plant 3 is discharged by means of the heat exchanger 7 to a respective associated boiler system 8, 9 and 10 for generating steam. The steam generated in the boiler systems 8, 9 and 10 is used to operate a high pressure steam turbine 11, a medium pressure steam turbine 12 and a low pressure steam turbine 13.

Die Hochdruckdampfturbine 11 und die Mitteldruckdampfturbine 12 sind mittels je einer der Dampfsammelleitungen 14 und 15 mit dem jeweils entsprechenden Dampfsystem 4 bzw. 5 gekoppelt. Die Mitteldruck-Zudampfsammelleitung 15 weist ferner einen Zwischenüberhitzer 20 auf, mittels dem ein Mitteldruck-Dampf zum Erhöhen des Wirkungsgrades der Dampfturbinenanlage 1 im Abhitzekessel 2 überhitzt wird. Der Mitteldruck-Dampf setzt sich zusammen aus dem in der Kesselanlage 9 erzeugten Mitteldruck-Zudampf und dem Abdampf der Hochdruckdampfturbine 11. Von dem Zwischenüberhitzer 20 strömt der überhitzte Mitteldruck-Dampf via die Mitteldruckdampfsammelleitung 22 zur Mitteldruckdampfturbine 12.The high-pressure steam turbine 11 and the medium-pressure steam turbine 12 are each coupled by means of one of the steam manifolds 14 and 15 with the respectively corresponding steam system 4 and 5 respectively. The medium-pressure Zudampfsammelleitung 15 further includes a reheater 20, by means of which a medium-pressure steam to increase the efficiency of the steam turbine plant 1 in the waste heat boiler 2 is overheated. The medium-pressure steam is composed of the medium-pressure Zudampf generated in the boiler system 9 and the exhaust steam of the high-pressure steam turbine 11. From the reheater 20, the superheated medium-pressure steam flows via the medium-pressure steam manifold 22 to the medium-pressure steam turbine 12th

Via eine Niederdruck-Zudampfsammelleitung 16 strömt der Niederdruck-Zudampf von der Kesselanlage 10 zu einer Umschaltarmatur 17. Der Druck des Zudampfs in der Niederdruck-Zudampfsammelleitung 16 beträgt vorliegend 4,2 bar. Im Falle einer Verwendung eines stark schwefelhaltigen Brennstoffs beim Betrieb der Gasturbinenanlage 3 wird der Druck des Niederdruck-Zudampfs derart erhöht, dass ein Auskondensieren von schwefliger Säure an den Wärmeübertragerflächen der Wärmeübertrager 7 und somit ein Korrodieren der Wärmeübertragerflächen verhindert wird. Dadurch ergibt sich in der Niederdruck-Zudampfsammelleitung 16 ein Druck von beispielsweise 8 bar.Via a low-pressure steam collecting line 16, the low-pressure Zudampf flows from the boiler system 10 to a changeover valve 17. The pressure of Zudampfs in the low-pressure Zudampfsammelleitung 16 is presently 4.2 bar. In the case of using a high sulfur-containing fuel during operation of the gas turbine plant 3, the pressure of the low-pressure Zudampfs is increased such that condensation of sulfurous acid on the heat transfer surfaces of the heat exchanger 7 and thus corroding the heat exchanger surfaces is prevented. This results in the low-pressure steam manifold 16, a pressure of, for example, 8 bar.

Die Niederdruck-Zudampfsammelleitung 16 weist ferner einen Niederdruck-Zudampfleitungsabschnitt 19 auf, an dem eine Zudampfeinleitstelle 21 ausgebildet ist. Via die Zudampfeinleitstelle 21 wird der Niederdruck-Zudampf über den Niederdruck-Zudampfleitungsabschnitt 19 mit dem Abdampf der Mitteldruckturbine 12 eingespeist.The low-pressure steam collecting line 16 also has a low-pressure Zudampfleitungsabschnitt 19, on which a Zudampfeinleitstelle 21 is formed. Via the Zudampfeinleitstelle 21 of the low-pressure Zudampf is fed via the low-pressure Zudampfleitungsabschnitt 19 with the exhaust steam of the medium-pressure turbine 12.

Der Umschaltarmatur 17 ist eine (nicht dargestellte) Steuerungseinrichtung zugeordnet, die eingerichtet ist, bei einem Unterschreiten des Abdampfdrucks der Mitteldruckdampfturbine 12 von einem vorgegebenen Soll-Wert, beispielsweise 4 bar, verursacht insbesondere durch einen Teillastbetrieb der Mitteldruckdampfturbine 12, die Umschaltarmatur 17 derart zu schalten, dass der Zudampf via die Umschaltarmatur 17 zu einer Einspeisedampfvorrichtung 18 strömt. Fällt beispielsweise der Betriebszustand der Mitteldruckdampfturbine 12 von einem Volllastbetrieb auf einen Teillastbetrieb von 60% der Volllast, fällt auch der Abdampfdruck entsprechend, d. h. der Abdampfdruck fällt auf 60% des Abdampfdrucks bei Volllast. Dadurch wird der Soll-Wert unterschritten und die Umschaltarmatur 17 wird geschaltet, wodurch der Zudampf zur Einspeisedampfvorrichtung 18 strömt, via die er als Einspeisedampf in die Mitteldruckturbine 12 strömt. Somit wird der Zudampf vom Druckniveau in der Niederdruck-Zudampfsammelleitung 16 auf das Druckniveau an der Zudampfeinleitstelle 21 in der Mitteldruckturbine 12 entspannt und somit energetisch verwertet.The reversing valve 17 is associated with a control device (not shown) which is set to switch the change-over valve 17 in such a way when the exhaust pressure of the medium-pressure steam turbine 12 falls below a predetermined desired value, for example 4 bar, caused in particular by a partial load operation of the medium-pressure steam turbine 12 in that the exhaust steam flows via the changeover valve 17 to a feed steam device 18. If, for example, the operating state of the medium-pressure steam turbine 12 drops from a full-load operation to a partial-load operation of 60% of the full load, the exhaust-steam pressure also drops accordingly, ie the exhaust-steam pressure drops to 60% of the exhaust-steam pressure at full load. As a result, the desired value is undershot and the change-over valve 17 is switched, whereby the spent steam flows to the feed steam device 18, via which it flows as feed steam into the medium-pressure turbine 12. Thus, the Zudampf from the pressure level in the low-pressure Zudampfsammelleitung 16 is relaxed to the pressure level at the Zudampfeinleitstelle 21 in the medium-pressure turbine 12 and thus energetically utilized.

Die Einspeisedampfvorrichtung 18 weist eine Mehrzahl an Dampfeinspeisestellen (nicht dargestellt) auf, von denen nur maximal eine angesteuert wird. Das heißt, die Dampfzufuhr erfolgt immer nur an einer Dampfeinspeisestelle. Dabei wird diejenige Dampfeinspeisestelle angesteuert, an der der Druck des Dampfturbinenprozessdampfs in etwa gleich dem Druck des Einspeisedampfs ist. Dies ermöglicht ein nahezu ungedrosseltes Einspeisen des Einspeisedampfs, wodurch ein zusätzlicher Drosselverlust durch Androsseln vermieden ist. Aufgrund von Strömungsverlusten weist der Zudampf nach Passieren der Umschaltarmatur 17 an der Dampfeinspeisestelle einen geringfügig niedrigeren Druck auf, als in der Niederdruck-Zudampfsammelleitung 16, beispielsweise 4 bar.The feed steam device 18 has a plurality of steam feed points (not shown), of which only a maximum of one is activated. That is, the steam is always supplied only at a Dampfeinspeisestelle. In this case, that steam feed point is controlled, at which the pressure of the steam turbine process steam is approximately equal to the pressure of the feed steam. This allows almost unthrottled feeding the feed steam, whereby an additional throttle loss is avoided by throttling. Due to flow losses, the Zudampf after passing the changeover valve 17 at the Dampfeinspeisestelle a slightly lower pressure than in the low pressure Zudampfsammelleitung 16, for example, 4 bar.

Ist der von der Steuerungseinrichtung gemessene Abdampfdruck über bzw. gleich dem Soll-Wert, wird die Umschaltarmatur 17 derart geschaltet, dass der Zudampfstrom via den Niederdruck-Zudampfleitungsabschnitt 19 zur Niederdruckdampfturbine 13 strömt. In dem Niederdruck-Zudampfleitungsabschnitt 19 strömen dann an der Zudampfeinleitstelle 21 der Abdampf der Mitteldruckturbine 12, der zuvor auf 4 bar entspannt wurde, und der Dampf der Niederdruck-Zudampfsammelleitung 16, der vorliegend ebenfalls einen Druck von 4 bar hat, zusammen und zur Niederdruckturbine 13.If the exhaust steam pressure measured by the control device is above or equal to the desired value, the changeover valve 17 is switched such that the exhaust steam flow flows via the low-pressure Zudampfleitungsabschnitt 19 to the low-pressure steam turbine 13. In the low-pressure Zudampfleitungsabschnitt 19 then flow at the Zudampfeinleitstelle 21 of the exhaust steam of the medium-pressure turbine 12, which was previously relaxed to 4 bar, and the steam of the low pressure Zudampfsammelleitung 16, which in this case also has a pressure of 4 bar together and to the low-pressure turbine thirteenth ,

Claims (9)

  1. Steam turbine plant (1) with an intermediate-pressure steam turbine (12) to which an intermediate-pressure inlet-steam collection line (15) is coupled and with a further inlet-steam collection line (16), having an inlet-steam line section (19), for supplying the intermediate-pressure steam turbine (12) or a low-pressure steam-turbine (13), characterized in that the inlet-steam collection line (16), at an inlet-steam introduction point (21) of the inlet-steam line section (19), is introduced into the exhaust-steam flow of the intermediate-pressure steam turbine (12) and a feed steam device (18) with at least one steam feed point formed on a stage of the intermediate-pressure steam turbine which is disposed on the exhaust-steam side is provided with a changeover valve (17) with which the feed steam device (18) is connected upstream of the inlet-steam introduction point (21) to the inlet-steam line section (19) and can be switched over in such a way that if the exhaust-steam pressure is lower than a setpoint pressure in the inlet-steam line section (19), the inlet-steam line section (19) is connected in a steam-conducting manner to the feed steam device (18) and is interrupted between the changeover valve (17) and the inlet-steam introduction point (21), and otherwise the feed steam device (18) is disconnected from the inlet-steam line section (19).
  2. Steam turbine plant (1) according to Claim 1,
    wherein the feed steam device (18) has a multiplicity of steam feed points on different stages of the intermediate-pressure steam turbine (12) and the feed steam device (18) can be activated in such a way that the supply of feed steam is carried out only at that steam feed point at which the pressure difference between the pressure at the introduction position inside the intermediate-pressure steam turbine (12) and feed steam itself is minimal.
  3. Steam turbine plant (1) according to Claim 2,
    wherein the feed steam device (18) is designed to, in the event of a load reduction of the intermediate-pressure steam turbine (12) transfer control from the steam feed point which is activated on a stage of the intermediate-pressure steam turbine (12) to an adjacent, upstream-disposed steam feed point.
  4. Steam turbine plant (1) according to Claim 2 or 3,
    wherein the feed steam device (18) is designed to, in the event of a load increase of the intermediate-pressure steam turbine (12), transfer control from the steam feed point which is activated on a stage of the intermediate-pressure steam turbine (12) to an adjacent downstream-disposed steam feed point.
  5. Steam turbine plant (1) according to one of Claims 1 to 4, wherein the characteristic curve of the opening degree of the changeover valve (17) for the connecting and disconnecting of the feed steam device (18) and/or the characteristic curve of the opening degree of the changeover valve for the connecting and disconnecting of the inlet-steam line section (19) is, or are, linear, progressive or degressive.
  6. Method for operating a steam turbine plant (1) according to one of Claims 1 to 5, with the steps:
    - making available of the steam turbine plant (1) according to one of Claims 1 to 5;
    - establishing of a setpoint pressure for the inlet-steam collection line (16);
    - switching over of the changeover valve (17) so that if the exhaust steam pressure is lower than the setpoint pressure in the inlet-steam line section (19), the inlet-steam line section (19) is connected in a steam-conducting manner to the feed steam device (18) and is interrupted between the changeover valve (17) and the inlet-steam introduction point (21); or
    - switching over of the changeover valve (17) so that if the exhaust steam pressure is equal to, or higher than, the setpoint pressure in the inlet-steam line section (19), the feed steam device (18) is disconnected from the changeover valve (17) and inlet steam is delivered directly from the inlet-steam line section (19) to the inlet-steam introduction point (21).
  7. Method according to Claim 6,
    wherein the feed steam device (18) has a multiplicity of steam feed points on different stages of the steam turbine (12) and the feed steam device (18) is activated in such a way that the supply of feed steam is carried out only at that steam feed point at which the pressure difference between the feed position inside the steam turbine and the feed steam is minimal.
  8. Method according to Claim 6 or 7,
    wherein, in the event of a load reduction of the intermediate-pressure steam turbine (12), control is transferred from the steam feed point which is activated on a stage of the intermediate-pressure steam turbine (12) to an adjacent, upstream-disposed steam feed point.
  9. Method according to one of Claims 6 to 8,
    wherein, in the event of a load increase of the steam turbine (12), control is transferred from the steam feed point which is activated on a stage of the intermediate-pressure steam turbine (12) to an adjacent, downstream-disposed steam feed point.
EP11771088.9A 2010-10-29 2011-10-12 Steam turbine plant with variable steam supply Not-in-force EP2611995B1 (en)

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EP2808501A1 (en) * 2013-05-27 2014-12-03 Siemens Aktiengesellschaft Method for operating a combined cycle power plant assembly
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EP2447484A1 (en) 2012-05-02
CN103201464B (en) 2016-02-03
EP2611995A1 (en) 2013-07-10
PL2611995T3 (en) 2017-09-29
US20130205749A1 (en) 2013-08-15
US9267394B2 (en) 2016-02-23
CN103201464A (en) 2013-07-10
WO2012055703A1 (en) 2012-05-03

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