EP0515911A1 - Méthode pour opérer une installation à turbines à gaz et à vapeur et une installation correspondante - Google Patents

Méthode pour opérer une installation à turbines à gaz et à vapeur et une installation correspondante Download PDF

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Publication number
EP0515911A1
EP0515911A1 EP92108102A EP92108102A EP0515911A1 EP 0515911 A1 EP0515911 A1 EP 0515911A1 EP 92108102 A EP92108102 A EP 92108102A EP 92108102 A EP92108102 A EP 92108102A EP 0515911 A1 EP0515911 A1 EP 0515911A1
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EP
European Patent Office
Prior art keywords
steam
gas
preheater
water
steam 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.)
Granted
Application number
EP92108102A
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German (de)
English (en)
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EP0515911B1 (fr
Inventor
Hermann Dr. Finckh
Hermann Brückner
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 AG
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Siemens AG
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Filing date
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Application filed by Siemens AG filed Critical Siemens AG
Publication of EP0515911A1 publication Critical patent/EP0515911A1/fr
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Publication of EP0515911B1 publication Critical patent/EP0515911B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01K23/106—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

Definitions

  • the invention relates to a method for operating a gas and steam turbine system with a steam generator through which the exhaust gas flows from the gas turbine for generating steam for a steam turbine in a water-steam cycle. It is also aimed at a gas and steam turbine plant operated using this method.
  • the amount of heat contained in the exhaust gas from the gas turbine is used to generate steam for the steam turbine.
  • the water-steam circuit of the steam turbine usually comprises two pressure stages, each of which is composed of a preheater and an evaporator and a superheater.
  • an intermediate superheater for re-overheating the steam leaving the high-pressure part of the steam turbine and a condensate preheater for heating up the condensed steam from the steam turbine are usually provided in the steam generator.
  • the amount of heat introduced into the steam generator differs in different operating states.
  • the amount of heat introduced into the steam generator is reduced, even if the mass flow of the exhaust gases of the gas turbine remains approximately constant.
  • the resulting reduction in the amount of steam produced results in a disproportionate reduction in the total amount of water available or the feed water flow, so that the temperature of the exhaust gases leaving the steam generator rises.
  • the efficiency of the system in the partial load range is lower than in the full load range, so that the overall efficiency of the system is only limited.
  • the invention is therefore based on the object of designing a method for operating a gas and steam turbine installation and such an installation in such a way that the highest possible overall efficiency is achieved in all operating states, in particular also in the part-load range.
  • this object is achieved according to the invention in that a partial amount of the water to be preheated is preheated outside the steam generator at the same high pressure, and in that the partial amount is set as a function of the total amount of water available in each case and is admixed with the water preheated in the steam generator. This creates a heat reservoir in the steam generator with an almost constant amount of heat in all operating states.
  • a further part of the water is evaporated at low pressure in the steam generator and mixed with the low-pressure steam flowing to a low-pressure part of the steam turbine with the amount of heat or heat output present in this heat reservoir.
  • the adjustable partial quantity is preheated in indirect heat exchange with steam from the steam turbine. This enables the adjustable partial quantity to be preheated to a temperature corresponding to the water preheated in the steam generator.
  • the object is achieved according to the invention in that the water Steam circuit includes a partial circuit connected in parallel to the preheater outside the steam generator, the throughput of which can be adjusted.
  • a heat exchanger for dissipating usable heat is arranged in the area of the preheater in the steam generator.
  • the heat exchanger is advantageously a low-pressure heating device, which is arranged in the flow direction of the exhaust gases behind the high-pressure heating device in the steam generator, and which is connected in parallel with the series connection of preheater and high-pressure heating device.
  • the throughput of the partial circuit can be regulated as a function of the amount of heat supplied to the steam generator. With this regulation, the throughput is reduced to the extent that the total amount of water available decreases due to reduced steam generation.
  • the available control range should be designed for a borderline case, eg for a throughput of zero in the partial load range.
  • a controllable valve is expediently connected in the partial circuit to adjust the throughput.
  • a heat exchanger through which an adjustable amount of steam flows is advantageously connected in the partial circuit.
  • a second preheater can also be connected downstream of the preheater arranged in the steam generator.
  • the partial circuit is expediently connected on the output side to the input of the second preheater.
  • heating surfaces are arranged in the steam generator in the flow direction of the exhaust gases behind the preheating device and are connected on the output side to the preheater and to the partial circuit.
  • the advantages achieved by the invention are, in particular, that a heat reservoir is created in the steam generator by means of an additional partial circuit connected in the water-steam circuit of the steam turbine, the throughput quantity of which can be adjusted, which independent of the operating state of the system, on the one hand, provides additional steam generation and on the other hand, in all load ranges, the temperature of the exhaust gases leaving the steam generator can be reduced to the low value achievable in the full load range. This achieves a high overall system efficiency.
  • FIG. 1 shows a schematic representation of an arrangement and circuit of a partial circuit according to the invention in the water-steam circuit of the steam turbine of a gas and steam turbine system.
  • the gas and steam turbine system comprises a gas turbine system 1a and a steam turbine system 1b.
  • the gas turbine system 1 a comprises a gas turbine 2 with a coupling Air compressor 3 and generator 4 and a combustion chamber 5 connected upstream of the gas turbine 2 and connected to a fresh air line 6 of the air compressor 3.
  • the steam turbine system 1b comprises a steam turbine 10 with a coupled generator 11 and, in a water-steam circuit 12, a condenser 13 connected downstream of the steam turbine 10 and a feed water tank 14 connected downstream of the condenser 13, and a steam generator 15.
  • an exhaust pipe 9 is connected to an inlet 15a of the steam generator 15.
  • the exhaust gas a leaves the steam generator 15 via its outlet 15b in the direction of a chimney (not shown).
  • the steam generator 15 comprises a condensate preheater or heating surfaces 20, a low-pressure heating device 21, two series-connected preheaters 22 and 23, a high-pressure heating device 24 and an intermediate superheater 25.
  • the condensate preheater 20 is connected on the input side via a line 30, into which a condensate pump 31 is connected, to the condenser 13 and on the output side via a line 32 to the feed water tank 14.
  • the preheater 22 is connected on the input side via a line 33, into which a valve 34 is connected, to a high-pressure pump 35, which is connected to the feed water tank 14.
  • the second preheater 23 connected downstream of the preheater 22 is connected on the output side to a water-steam container 37 of the high-pressure heating device 24 via a first branch 36.
  • the preheater 23 is also connected to a water-steam separation vessel 40 via a further branch 38, into which a corner valve 39 is connected.
  • the high-pressure heating device 24 comprises an evaporator 45 which is connected to the water-steam container 37 via a circulation line 46.
  • a pump 47 is connected to the circulation line 46.
  • the high-pressure heating device 24 also comprises a superheater 48 which is connected on the inlet side to the water-steam container 37 and on the outlet side via a live steam line 49 to a high-pressure part 10a of the steam turbine 10.
  • the high-pressure part 10a of the steam turbine 10 is connected on the output side via a steam line 50 both to the reheater 25 and to the water-steam separation vessel 40.
  • the intermediate superheater 25 is connected on the outlet side via a steam line 51 to a medium pressure part 10b of the steam turbine 10.
  • a low-pressure part 10c of the steam turbine 10 is connected downstream of the medium-pressure part 10b.
  • the turbine parts 10a, 10b and 10c of the steam turbine 10 drive the generator 11 via a common shaft 52.
  • the low-pressure heating device 21 comprises an evaporator 60 which is connected to a water-steam container 63 via a circulation line 61 with a pump 62.
  • the low-pressure heating device 21 also comprises a superheater 64 which is connected on the inlet side via a steam line 65 both to the water-steam container 63 and to a water-steam separation vessel 86.
  • the superheater 64 is connected on the output side via a steam line 67 to the low-pressure part 10c of the steam turbine 10.
  • the water-steam tank 63 is connected to the feed water tank 14 via a line 66.
  • a low-pressure pump 68 is connected in line 66.
  • the water-steam circuit 12 of the steam turbine 10 comprises a partial circuit 70 which extends outside the steam generator 15 and which is connected in parallel with the preheater 22 arranged in the steam generator 15.
  • the partial circuit 70 is on the input side via the high-pressure pump 35 to the feed water tank 14 and on the output side in the area between the preheaters 22 and 23 the preheater 22 connected.
  • a heat exchanger 71 is connected in the partial circuit 70.
  • the heat exchanger 71 is connected on the primary side via a steam line 72 to the low-pressure part 10c of the steam turbine 10 and via a water line 73 to the feed water tank 14.
  • a control valve 74 is connected to the sub-circuit 70, to which a control signal s can be fed via a signal line 75.
  • the combustion chamber 5 is supplied with coal k via a feed line 7 in a manner not shown in detail.
  • the coal k is burned in the combustion chamber 5 with the compressed fresh air 1 from the air compressor 3.
  • the hot flue gas g formed during the combustion is passed into the gas turbine 2 via a flue gas line 8. There it relaxes and drives the gas turbine 2. This in turn drives the air compressor 3 and the generator 4.
  • the hot exhaust gases a emerging from the gas turbine are introduced into the steam generator 15 via the exhaust line 9 and are used there to generate steam for the steam turbine.
  • the steam emerging from the low-pressure part 10c of the steam turbine 10 is fed to the condenser 13 via a steam line 80 and condenses there.
  • the condensate is pumped into the condensate preheater 20 via the pump 31 and warmed up there.
  • the heated condensate flows out of the condensate preheater 20 via the line 32 into the feed water tank 14.
  • the feed water from the feed water tank 14 is pumped via the pump 35 both into the preheater 22 and into the partial circuit 70.
  • the partial quantity t2 flowing through the preheater 22 can be adjusted with the valve 34.
  • the partial or throughput quantity t1 of the feed water flowing through the partial circuit 70 is set with the control valve 74 and mixed with the feed water preheated in the preheater 22.
  • the partial quantity t1 of the feed water flowing in the pitch circle 70 is passed through indirect heat exchange with steam from the low pressure part 10c of the steam turbine 10 to the temperature corresponding to the preheater 22 preheated portion t2 of the feed water.
  • the preheated feed water flows through the second preheater 23 and is fed via line 36 into the water-steam container 37 of the high-pressure heating device 24. There, the preheated feed water collected in the water-steam container 37 flows through the evaporator 45, which is heated by the hot exhaust gas a, and is thereby evaporated.
  • the steam separated in the water-steam container 37 flows through the superheater 48 heated by the exhaust gas a and is fed via the live steam line 49 in the superheated state at a pressure of approximately 110 bar to the high-pressure part 10a of the steam turbine 10.
  • the steam released in the high-pressure part 10a flows through the reheater 25 at a pressure of approximately 30 bar and is then expanded to a pressure of approximately 3 bar in the medium-pressure part 10b of the steam turbine 10.
  • a part of the steam released in the high pressure part 10a flows via the steam line 50 as so-called wet steam into the water-steam separation vessel 40.
  • the steam which is still under a pressure of about 30 bar, is separated from the water.
  • the water can be introduced into the water-steam separation vessel 86 via a line 81 into which a valve 82 is connected.
  • the pressure in the water-steam separation vessel 86 is approximately 3 bar, so that the water flowing in via line 81 evaporates immediately.
  • the water separated in the water-steam separation vessel 86 is fed to the feed water tank 14 via a line 83.
  • the steam separated in the water-steam separation vessel 86 is fed to the low-pressure heating device 21.
  • Another portion t3 of the feed water is pumped from the feed water tank 14 into the water-steam tank 63 of the low-pressure heating device 21 via the low-pressure pump 68.
  • the feed water is pumped through the pump 62 through the evaporator 60 and back into the water-steam container 63.
  • the steam generated is together with the steam flowing out of the water-steam separation vessel 86 overheats in the superheater 64 and is fed via the steam line 67 to the low pressure part 10c of the steam turbine 10.
  • the steam is expanded together with the steam flowing out of the medium pressure part 10b and fed to the condenser 13 via the steam line 80.
  • the preheater 22 created a heat reservoir.
  • This heat reservoir is advantageously used to generate steam for the low-pressure part 10c of the steam turbine 10.
  • the heat reservoir can also e.g. can be used to generate steam for the medium pressure part 10b of the steam turbine 10 or as an additional preheating stage.
  • the partial amount t2 of the feed water flowing through the preheater 22 arranged in the steam generator 15 is set to the amount of water available during partial load operation, so that the additional partial amount t1 available under full load operation is passed through the partial circuit 70.
  • the partial or throughput quantity t1 of the partial circuit 70 is set such that the partial quantity t2 flowing through the preheater 22 is approximately constant in all operating states.
  • the throughput quantity t1 flowing in the pitch circle 70 is therefore expediently set as a function of the total water quantity available.
  • Another expedient control variable is the amount of heat introduced into the steam generator 15 with the exhaust gases a and, if appropriate, with the flue gases additionally generated in a steam generator with additional firing. A signal s corresponding to these control variables is fed to the control valve 74 via a control line 75 in a manner not shown in detail.
  • the partial or throughput quantity t1 in the partial circle 70 is approximately 30 to 50%, preferably 40%, of the total water quantity.
  • the additional firing is first withdrawn in the case of a steam generator with additional firing and the power of the gas turbine 2 is only lowered as a further measure.
  • the power of the gas turbine 2 is immediately reduced when the load is removed. In both cases, the amount of heat introduced into the steam generator 15 drops, so that the total amount of feed water available decreases due to the lower steam generation.
  • the partial quantity t2 flowing through the preheater 22 in the steam generator 15 remains constant, although the feed water quantity is reduced overall.
  • the control valve 74 is closed continuously as the load decreases.
  • the amount of steam supplied to the heat exchanger 71 on the primary side is reduced to zero in the part-load range. This measure ensures that the low-pressure heating device 21 continuously generates steam, so that the temperature of the exhaust gases a in the flow direction behind the evaporator 60 remains approximately constant over the entire load range.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP92108102A 1991-05-27 1992-05-13 Méthode pour opérer une installation à turbines à gaz et à vapeur et une installation correspondante Expired - Lifetime EP0515911B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4117313 1991-05-27
DE4117313 1991-05-27

Publications (2)

Publication Number Publication Date
EP0515911A1 true EP0515911A1 (fr) 1992-12-02
EP0515911B1 EP0515911B1 (fr) 1996-03-13

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EP92108102A Expired - Lifetime EP0515911B1 (fr) 1991-05-27 1992-05-13 Méthode pour opérer une installation à turbines à gaz et à vapeur et une installation correspondante

Country Status (4)

Country Link
US (1) US5269130A (fr)
EP (1) EP0515911B1 (fr)
DE (1) DE59205640D1 (fr)
RU (1) RU2062332C1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19539756A1 (de) * 1995-07-27 1997-01-30 Soon Ong Tiong Ad-/Desorptionskühlverfahren zur Kraftwerksleistungssteigerung
WO1997007323A1 (fr) * 1995-08-18 1997-02-27 Siemens Aktiengesellschaft Installation a turbine a gaz et a vapeur et procede de fonctionnement de ladite installation ainsi que generateur de vapeur de chaleur perdue pour une telle installation
EP0767290A1 (fr) * 1995-10-02 1997-04-09 Asea Brown Boveri Ag Procédé de fonctionnement d'une centrale d'énergie
DE19645322A1 (de) * 1996-11-04 1998-05-07 Asea Brown Boveri Kombinierte Kraftwerksanlage mit einem Zwangsdurchlaufdampferzeuger als Gasturbinen-Kühlluftkühler

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Publication number Priority date Publication date Assignee Title
DE4029991A1 (de) * 1990-09-21 1992-03-26 Siemens Ag Kombinierte gas- und dampfturbinenanlage
DE19527537C1 (de) * 1995-07-27 1996-09-26 Siemens Ag Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage sowie danach arbeitende Anlage
US6230480B1 (en) 1998-08-31 2001-05-15 Rollins, Iii William Scott High power density combined cycle power plant
US6968700B2 (en) 2001-03-01 2005-11-29 Lott Henry A Power systems
US6467273B1 (en) 2001-03-01 2002-10-22 Henry A. Lott Method for producing electrical power
US6841683B2 (en) * 2001-08-30 2005-01-11 Teva Pharmaceutical Industries Ltd. Sulfonation method for zonisamide intermediate in zonisamide synthesis and their novel crystal forms
EP1388643B1 (fr) * 2002-08-09 2008-10-29 Hitachi, Ltd. Centrale combinée
US20070130952A1 (en) * 2005-12-08 2007-06-14 Siemens Power Generation, Inc. Exhaust heat augmentation in a combined cycle power plant
US8544273B2 (en) * 2008-09-17 2013-10-01 Siemens Concentrated Solar Power Ltd. Solar thermal power plant
US20110210555A1 (en) * 2010-02-26 2011-09-01 Xia Jian Y Gas turbine driven electric power system with constant output through a full range of ambient conditions
US20120234263A1 (en) * 2011-03-18 2012-09-20 Uop Llc Processes and systems for generating steam from multiple hot process streams
US9404393B2 (en) * 2011-03-24 2016-08-02 General Electric Company Combined cycle power plant
US9863266B2 (en) * 2015-11-19 2018-01-09 Borgwarner Inc. Waste heat recovery system for a power source
US10174639B2 (en) * 2017-01-31 2019-01-08 General Electric Company Steam turbine preheating system
US10337357B2 (en) 2017-01-31 2019-07-02 General Electric Company Steam turbine preheating system with a steam generator

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EP0410111A1 (fr) * 1989-07-27 1991-01-30 Siemens Aktiengesellschaft Chaudière de récupération de chaleur pour une centrale à turbine à gaz et à vapeur

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DE1426443A1 (de) * 1962-09-21 1969-03-27 Siemens Ag Waermekraftanlage
DE2023748A1 (de) * 1969-05-14 1971-02-18 Stein Industrie Verfahren fur die Verbesserung der Betriebsweise einer einen kombinierten Kreislauf aufweisenden Gas und Dampf turbmenanlage mit nachgeschaltetem Dampfkessel und Anlage zur Durchfuhrung des Verfahrens
EP0410111A1 (fr) * 1989-07-27 1991-01-30 Siemens Aktiengesellschaft Chaudière de récupération de chaleur pour une centrale à turbine à gaz et à vapeur

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19539756A1 (de) * 1995-07-27 1997-01-30 Soon Ong Tiong Ad-/Desorptionskühlverfahren zur Kraftwerksleistungssteigerung
DE19539756C2 (de) * 1995-07-27 1999-09-02 Soon Ad-/Desorptionskühlverfahren zur Kraftwerksleistungssteigerung
WO1997007323A1 (fr) * 1995-08-18 1997-02-27 Siemens Aktiengesellschaft Installation a turbine a gaz et a vapeur et procede de fonctionnement de ladite installation ainsi que generateur de vapeur de chaleur perdue pour une telle installation
EP0767290A1 (fr) * 1995-10-02 1997-04-09 Asea Brown Boveri Ag Procédé de fonctionnement d'une centrale d'énergie
DE19536839A1 (de) * 1995-10-02 1997-04-30 Abb Management Ag Verfahren zum Betrieb einer Kraftwerksanlage
US5839269A (en) * 1995-10-02 1998-11-24 Asea Brown Boveri Ag Method of operating a combined gas and power steam plant
DE19645322A1 (de) * 1996-11-04 1998-05-07 Asea Brown Boveri Kombinierte Kraftwerksanlage mit einem Zwangsdurchlaufdampferzeuger als Gasturbinen-Kühlluftkühler
US6018942A (en) * 1996-11-04 2000-02-01 Asea Brown Boveri Ag Combined cycle power station with gas turbine cooling air cooler
DE19645322B4 (de) * 1996-11-04 2010-05-06 Alstom Kombinierte Kraftwerksanlage mit einem Zwangsdurchlaufdampferzeuger als Gasturbinen-Kühlluftkühler

Also Published As

Publication number Publication date
EP0515911B1 (fr) 1996-03-13
US5269130A (en) 1993-12-14
DE59205640D1 (de) 1996-04-18
RU2062332C1 (ru) 1996-06-20

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