WO1995000747A1 - Procede permettant de faire fonctionner une installation a turbine a gaz et a turbine a vapeur et installation a turbine a gaz et a turbine a vapeur fonctionnant selon ledit procede - Google Patents

Procede permettant de faire fonctionner une installation a turbine a gaz et a turbine a vapeur et installation a turbine a gaz et a turbine a vapeur fonctionnant selon ledit procede Download PDF

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Publication number
WO1995000747A1
WO1995000747A1 PCT/DE1994/000657 DE9400657W WO9500747A1 WO 1995000747 A1 WO1995000747 A1 WO 1995000747A1 DE 9400657 W DE9400657 W DE 9400657W WO 9500747 A1 WO9500747 A1 WO 9500747A1
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WO
WIPO (PCT)
Prior art keywords
fuel
steam
water
pressure
stage
Prior art date
Application number
PCT/DE1994/000657
Other languages
German (de)
English (en)
Inventor
Marcel Moricet
Bert Rukes
Original Assignee
Siemens Aktiengesellschaft
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 Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO1995000747A1 publication Critical patent/WO1995000747A1/fr

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/20—Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products
    • F02C3/30—Adding water, steam or other fluids for influencing combustion, e.g. to obtain cleaner exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22—Fuel supply systems
    • F02C7/224—Heating fuel before feeding to the burner
    • 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 operating a gas and steam turbine plant (CCGT plant) in which the heat contained in the relaxed working medium from the gas turbine is used to generate steam for the steam turbine connected to a water-steam circuit . It continues to focus on a combined cycle plant that uses this process.
  • CCGT plant gas and steam turbine plant
  • the heat contained in the relaxed working fluid from the gas turbine is used to generate steam for the steam turbine.
  • the heat transfer takes place in a steam generator or waste heat boiler downstream of the gas turbine, in which heating surfaces are arranged in the form of tubes or tube bundles. These in turn are switched into the water-steam cycle of the steam turbine.
  • the water-steam cycle comprises several, for example two, pressure stages, each pressure stage having a preheating, an evaporator and a superheater heating surface.
  • a thermodynamic efficiency of about 50% to 55% is achieved, depending on the pressure conditions prevailing in the water-steam cycle of the steam turbine.
  • the invention is based on the object of specifying a method for operating such a gas and steam turbine installation with which an increase in the thermodynamic efficiency is achieved. In a suitable gas and steam turbine plant, this should be achieved with particularly simple means.
  • the stated object is achieved according to the invention in that a is preheated by means of fuel used for the gas turbine.
  • the fuel is preheated advantageously by indirect heat exchange of the fuel with a partial flow of preheated water taken from the water-steam cycle of the steam turbine, which water is returned to the water-steam cycle after the heat has been exchanged with the fuel.
  • the partial flow for heating the fuel is expediently taken from either a high-pressure stage or a low-pressure stage of the water-steam cycle.
  • a partial flow is taken from both the high-pressure stage and the low-pressure stage and used for a two-stage fuel heating.
  • the fuel is moistened and heated by direct heat exchange with preheated water.
  • the water used for humidification is preheated by indirect heat exchange with the first partial stream taken from the low-pressure stage of the water-steam cycle.
  • the heated fuel is then further heated by indirect heat exchange with the second partial stream taken from the high-pressure stage of the water-steam cycle.
  • the fuel is preheated to a temperature of 100 ° C. to 400 ° C.
  • the fuel is advantageously preheated to a temperature of approximately 150 ° C.
  • the fuel is preheated to a temperature of approximately 280 ° C. to 320 ° C.
  • the fuel is preheated to a temperature of likewise 280 ° C to 320 ° C.
  • the above object is achieved in that a heat exchanger is provided for fuel preheating, which is connected on the primary side in the water-steam cycle and on the secondary side in the fuel line.
  • the heat exchanger is advantageously connected in parallel with the condensate preheater on the primary side.
  • the preheated water of the partial flow used to preheat the fuel is at low pressure.
  • the heat exchanger can also be connected in parallel with the high-pressure preheater, so that the preheated water of the partial flow serving to preheat the fuel is at a correspondingly high pressure.
  • a further heat exchanger is expediently provided, which is arranged on the secondary side in the flow direction of the fuel upstream of the first heat exchanger. It is also connected on the primary side to the low-pressure stage of the water-steam cycle and is parallel to the condensate preheater, while the first heat exchanger is connected to the high-pressure stage of the water-steam cycle for further heating of the fuel and is parallel to the high-pressure preheater.
  • the preheating of the fuel in the first stage is expediently carried out by moistening the fuel by means of preheated water conducted in a water circuit.
  • a fuel humidifier is connected in the fuel line, in which the fuel and the preheated water are guided in counterflow to one another.
  • the preheating of the The water serving as fuel is humidified in the further heat exchanger connected to the low-pressure stage of the water-steam cycle.
  • FIGS. 1 and 2 a gas and steam turbine system with a heat exchanger connected at alternative points to a water-steam circuit of the steam turbine for preheating Bren s off, and
  • Figure 3 shows a gas and steam turbine system according to Figures 1 and 2 with two heat exchangers for fuel moistening and - preheating.
  • a gas and steam turbine plant according to FIGS. 1 to 3 comprises a gas turbine plant 1 a and a steam turbine plant 1 b.
  • the gas turbine system 1 a comprises a gas turbine 2 with a coupled air compressor 3 and a combustion chamber 4 connected upstream of the gas turbine 2 and which is connected to a fresh air line 5 of the air compressor 3.
  • a fuel line 6 opens into the combustion chamber 4 of the gas turbine 2.
  • the gas turbine 2 and the air compressor 3 as well as a generator 7 sit on a common shaft 8.
  • the steam turbine system 1b comprises a steam turbine 10 with a coupled generator 11 and, in a water-steam circuit 12, a capacitor 13 connected downstream of the steam turbine 10 and a waste heat steam generator 14.
  • the steam turbine 10 consists of a high-pressure part 10a and a low-pressure part 10b, which drive the generator 11 via a common shaft 15.
  • An exhaust pipe 17 is connected to an inlet 14a of the heat recovery steam generator 14 for supplying working medium AM ′ or flue gas relaxed in the gas turbine 2 to the heat recovery steam generator 14.
  • the relaxed working medium AM 1 from the gas turbine 2 leaves the heat recovery steam generator 14 via its outlet 14b in the direction of a chimney (not shown).
  • the steam generator 14 comprises a condensate preheater 20 and a low-pressure evaporator 22 as well as a low-pressure superheater 24. It also comprises in a high-pressure stage of the water-steam circuit 12 a high-pressure preheater or economizer 26, a high-pressure evaporator 28 and a high-pressure superheater 30.
  • the low-pressure superheater 24 is connected to the low-pressure part 10b of the steam turbine 10 via a steam line 32.
  • the high-pressure superheater 30 is connected to the high-pressure part 10 a of the steam turbine 10 via a steam line 34.
  • the low-pressure part 10b of the steam turbine 10 is connected on the output side to the condenser 13 via a steam line 36.
  • the water-steam circuit 12 shown in FIGS. 1 to 3 is thus made up of two pressure stages. However, it can also be constructed from three pressure stages.
  • the waste heat steam generator 14 additionally has a medium-pressure evaporator and a medium-pressure superheater, which are connected to the water-steam circuit 12 and are connected to a medium-pressure part of the steam turbine 10.
  • the condenser 13 is connected to the condensate preheater 20 via a condensate line 42.
  • a condensate pump 44 is located in the condensate line 42.
  • the condensate preheater 20 is connected on the outlet side to a feed water tank 46.
  • the feed water tank 46 is connected on the output side via a low pressure pump 48 to a water / steam separation vessel 50 of the low pressure stage.
  • the low-pressure superheater 24 and - via a circulation pump 52 - the low-pressure evaporator 22 are connected to this vessel 50.
  • the feed water tank 46 is also connected on the output side via a high-pressure pump 54 to the economizer 26, which in turn is connected on the output side to a water-steam separation vessel 56 of the high-pressure stage.
  • the high-pressure superheater 30 and - via a circulating pump 58 - the high-pressure evaporator 28 are connected to the vessel 56.
  • a steam line 60 connected to the steam line 32 also opens into the feed water tank 46.
  • the feed water tank 46 is connected to the condensate line 42 via a circulation pump 59.
  • the secondary side of a heat exchanger 62 is connected into the fuel line 6 and, according to FIG. 1, is connected in parallel with the condensate preheater 20.
  • the heat exchanger 62 is connected on the primary side via an inflow line 64 to the feed water tank 46 and via an outflow line 66 to the condensate line 42.
  • a pump 68 is connected to the inflow line 64.
  • a throttle 70 is connected in the outflow line 66.
  • a heat exchanger 62 ' is connected in parallel with the economizer 26 on the primary side.
  • the heat exchanger 62 ' is connected on the primary side via an inflow line 64' to the outlet of the economizer 26 and via an outflow line 66 'to the suction side of the high-pressure pump 54.
  • a throttle 70 ' is connected in the outflow line 66'.
  • the combustion chamber 4 is supplied with liquid or gaseous fuel BS, for example natural gas or heating oil, via the fuel line 6.
  • the fuel BS is preheated in the heat exchanger 62, 62 'to a temperature T ] _ of 100 ° C. to 400 ° C.
  • the preheated fuel BS is used to generate the Working medium AM for the gas turbine 2 in the combustion chamber 4 burns with compressed fresh air L from the air compressor 3.
  • the hot and high-pressure working medium AM or flue gas that arises during the combustion is expanded in the gas turbine 2 and drives it and the air compressor 3 and the generator 7.
  • the relaxed working medium AM 'emerging from the gas turbine 2 with a temperature T2 of approximately 550 ° C. is introduced into the waste heat steam generator 14 via the exhaust gas line 17 and used there to generate steam for the steam turbine 10.
  • the flue gas stream and the water-steam circuit 12 are linked to one another in countercurrent.
  • vapors are generated at different pressure levels, the enthalpy of which is used to generate electricity in the steam turbine 10.
  • steam can be generated with a pressure p N of 6 bar and a temperature T N of 200 ° C.
  • steam can be generated with a pressure p H of 80 bar and a temperature T H of 520 ° C.
  • the expanded steam emerging from the low-pressure part 10b of the steam turbine 10 is fed to the condenser 13 via the steam line 36 and condenses there.
  • the condensate is pumped into the condensate preheater 20 via the condensate pump 44 and preheated there.
  • the preheated condensate flows into the feed water tank 46.
  • a partial stream t 1 of the preheated feed water which is at low pressure is removed from the feed water tank 46 via the inflow line 64.
  • This partial flow t ] _ is first brought to a pressure above the fuel pressure by means of the pump 68 and then fed to the heat exchanger 62. There, the heat contained in the partial flow t_ of the preheated feed water is transferred to the fuel BS by indirect heat exchange.
  • the partial flow t 1 of the cooled feed water which is conducted via the outflow line 66 is first throttled and then mixed with the condensate flowing via the condensate line 42.
  • the fuel is preheated at a fuel pressure p BS of 5 to 20 bar.
  • the partial flow t] _ of the preheated feed water is brought to a pressure above the fuel pressure by means of the pump 68.
  • fuel preheating to a temperature T of about 150 ° C. is achieved.
  • preheated feed water under high pressure is fed to the heat exchanger 62 '.
  • a partial flow t ′ ⁇ of the preheated feed water, which is under high pressure, is removed from the economizer 26 via the discharge line 64 ′.
  • the partial flow t'i is conducted via the discharge line 66 'and, after throttling in the throttle 70', the water-steam circuit 12 of the steam turbine 10 between the feed water tank 46 and fed to the high pressure pump 54 again.
  • a two-stage fuel preheating takes place.
  • the fuel BS is heated to a temperature T3 of approximately 130 ° C. to 150 ° C.
  • the fuel is heated in a fuel humidifier 80 connected to the fuel line 6 by direct heat exchange with heated water UW flowing in a water circuit 82.
  • the circulating water UW is heated by indirect heat exchange in a further heat exchanger 83 connected on the secondary side in the water circuit 82.
  • the heat exchanger 83 is connected on the primary side to the water-steam circuit 12 of the steam turbine.
  • a partial flow t ′′ 1 of the preheated feed water is taken from the feed water tank 46, similarly to the exemplary embodiment according to FIG. 1, via an inflow line 64 ′′ and a pump 68 ′′.
  • the partial flow t ′′ 1 is fed back to the water-steam circuit 12 via an outflow line 66 ′′ connected to the condensate preheater 22.
  • the heat exchanger 83 is located at least in part of the condensate preheater 20 parallel.
  • the fuel BS fed to the fuel humidifier 80 in the manner of a countercurrent column at the sump 84 is saturated from below with the water UW trickling down from the head 86 in the countercurrent.
  • the pressure, temperature and throughput of the circulating water UW depend on the minimally achievable degree of saturation of the fuel BS and on the minimum required sprinkling density within the fuel humidifier 80, so that only part of the water UW used evaporates. This part is fresh water FW replaced, which is fed via a fresh water line 88 to the water circuit 82, into which a pump 90 is connected.
  • the fuel BS heats up from below, while the water UW cools down from above.
  • the water UW emerging at the sump 84 of the fuel humidifier 80 is mixed with the fresh water FW and heated by indirect heat exchange with the partial flow t ′′ ′′ of the preheated feed water.
  • Pressure, temperature and quantity per unit of time of the partial flow t ⁇ _ • ⁇ depend on the operating state of the fuel humidifier 80 and are selected such that the water temperature at the head 86 of the fuel humidifier 80 above the saturation state of the the heated fuel BS 'leaving the humidifier 80.
  • the on the temperature T3 of e.g. 150 ° C heated fuel BS ' is further heated in a second stage by means of a heat exchanger 62' 'to a temperature T] _ of 250 ° C to 320 ° C.
  • the heat exchanger 62 * ' which is connected downstream of the fuel humidifier 80 in the fuel line 6, is connected on the primary side - as in the exemplary embodiment according to FIG. 2 - to the high-pressure stage of the water-steam circuit 12 of the steam turbine 10.
  • the further heating of the fuel BS ' takes place by indirect heat exchange with a partial stream t2 of the preheated feed water which is under high pressure and which is taken from the high pressure stage.
  • This partial flow t2 is fed to the heat exchanger 62 ′′ via a feed line 64 ′′ ′′ connected to the high-pressure preheater 26. After the heat exchange and subsequent throttling in the throttle 70 '' 'lying in an outflow line 66' '', the partial flow t2 is fed to the condensate preheater 20.

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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)

Abstract

L'invention concerne un procédé permettant de faire fonctionner une installation à turbine à gaz et à turbine à vapeur (1a, 1b) dans laquelle la chaleur contenue dans les gaz actifs (AM') détendus, qui sortent de la turbine à gaz (2) servent à produire de la vapeur pour alimenter la turbine à vapeur (10) montée dans un circuit eau-vapeur (12). Afin d'augmenter le rendement thermique, il est prévu de préchauffer un combustible (BS) utilisé pour produire les gaz actifs (AM) qui entraînent la turbine à gaz (2). L'installation (1a, 1b) comprend une chambre de combustion (4) montée en amont de la turbine à gaz (2), qui comporte une conduite de combustible (6) qui passe par un échangeur thermique (62, 62') raccordé au circuit eau-vapeur (12).
PCT/DE1994/000657 1993-06-24 1994-06-13 Procede permettant de faire fonctionner une installation a turbine a gaz et a turbine a vapeur et installation a turbine a gaz et a turbine a vapeur fonctionnant selon ledit procede WO1995000747A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19934321081 DE4321081A1 (de) 1993-06-24 1993-06-24 Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage sowie danach arbeitende GuD-Anlage
DEP4321081.3 1993-06-24

Publications (1)

Publication Number Publication Date
WO1995000747A1 true WO1995000747A1 (fr) 1995-01-05

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PCT/DE1994/000657 WO1995000747A1 (fr) 1993-06-24 1994-06-13 Procede permettant de faire fonctionner une installation a turbine a gaz et a turbine a vapeur et installation a turbine a gaz et a turbine a vapeur fonctionnant selon ledit procede

Country Status (2)

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DE (1) DE4321081A1 (fr)
WO (1) WO1995000747A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6041588A (en) * 1995-04-03 2000-03-28 Siemens Aktiengesellschaft Gas and steam turbine system and operating method
GB2360820A (en) * 2000-02-14 2001-10-03 Alstom Heat-recovery fuel preheat system in a combined-cycle power plant
CN1313714C (zh) * 2000-07-25 2007-05-02 西门子公司 运行燃气和蒸汽轮机装置的方法及相应的装置
CN1325770C (zh) * 2000-10-17 2007-07-11 西门子公司 组合式燃气和蒸汽轮机设备中用于预热燃料的装置和方法
CN101644192A (zh) * 2008-08-05 2010-02-10 通用电气公司 在联合循环动力设备中提取热水来预热燃料的系统和组件
US10100680B2 (en) 2013-09-19 2018-10-16 Siemens Aktiengesellschaft Combined cycle gas turbine plant comprising a waste heat steam generator and fuel preheating step
US11118781B2 (en) 2016-07-19 2021-09-14 Siemens Energy Global GmbH & Co. KG Vertical heat recovery steam generator

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US5357746A (en) * 1993-12-22 1994-10-25 Westinghouse Electric Corporation System for recovering waste heat
WO1996036793A1 (fr) * 1995-05-18 1996-11-21 Westinghouse Electric Corporation Systeme de turbine a gaz a injection de vapeur equipe d'un dispositif de compression de vapeur
DE19532081A1 (de) * 1995-08-31 1997-03-06 Abb Management Ag Verfahren zum Betrieb einer Kombianlage
DE19536839A1 (de) * 1995-10-02 1997-04-30 Abb Management Ag Verfahren zum Betrieb einer Kraftwerksanlage
DE19544226B4 (de) * 1995-11-28 2007-03-29 Alstom Kombianlage mit Mehrdruckkessel
DE59711190D1 (de) * 1997-11-19 2004-02-12 Alstom Switzerland Ltd Verfahren und Vorrichtung zur Brennstoffvorwärmung einer Feuerungsanlage
JP3897891B2 (ja) * 1998-01-19 2007-03-28 株式会社東芝 コンバインドサイクル発電プラント
DE19829088C2 (de) * 1998-06-30 2002-12-05 Man Turbomasch Ag Ghh Borsig Stromerzeugung in einem Verbundkraftwerk mit einer Gas- und einer Dampfturbine
DE19837251C1 (de) * 1998-08-17 2000-02-10 Siemens Ag Gas- und Dampfturbinenanlage
DE60033738T2 (de) * 1999-07-01 2007-11-08 General Electric Co. Vorrichtung zur Befeuchtung und Heizung von Brenngas
DE19943782C5 (de) * 1999-09-13 2015-12-17 Siemens Aktiengesellschaft Gas- und Dampfturbinenanlage
DE10056128A1 (de) 2000-11-13 2002-06-06 Alstom Switzerland Ltd Verfahren zum Betreiben einer Gasturbinenanlage sowie eine dementsprechende Anlage
EP1483490A1 (fr) * 2002-03-14 2004-12-08 Alstom Technology Ltd Systeme de production d'energie
DE102007054467B4 (de) * 2007-11-13 2009-09-10 Triesch, Frank, Dr. Ing. Verfahren zur Brennstoffvorwärmung
EP2426337A1 (fr) * 2010-09-03 2012-03-07 Siemens Aktiengesellschaft Dispositif de préchauffage de carburant et procédé de préchauffage de carburant

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EP0391082A2 (fr) * 1989-04-03 1990-10-10 Westinghouse Electric Corporation Centrale thermique à cycle combiné
EP0588392A1 (fr) * 1992-07-13 1994-03-23 N.V. Kema Centrale avec turbines à gaz et à vapeur utilisant du gaz naturel humidifié

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EP0086504A2 (fr) * 1982-02-16 1983-08-24 Shell Internationale Researchmaatschappij B.V. Procédé de production de force mécanique
JPS60198337A (ja) * 1984-03-19 1985-10-07 Toshiba Corp ガスタ−ビンの燃料系統加熱装置
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EP0588392A1 (fr) * 1992-07-13 1994-03-23 N.V. Kema Centrale avec turbines à gaz et à vapeur utilisant du gaz naturel humidifié

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6041588A (en) * 1995-04-03 2000-03-28 Siemens Aktiengesellschaft Gas and steam turbine system and operating method
GB2360820A (en) * 2000-02-14 2001-10-03 Alstom Heat-recovery fuel preheat system in a combined-cycle power plant
CN1313714C (zh) * 2000-07-25 2007-05-02 西门子公司 运行燃气和蒸汽轮机装置的方法及相应的装置
CN1325770C (zh) * 2000-10-17 2007-07-11 西门子公司 组合式燃气和蒸汽轮机设备中用于预热燃料的装置和方法
CN101644192A (zh) * 2008-08-05 2010-02-10 通用电气公司 在联合循环动力设备中提取热水来预热燃料的系统和组件
CN101644192B (zh) * 2008-08-05 2014-04-02 通用电气公司 在联合循环动力设备中提取热水来预热燃料的系统和组件
US10100680B2 (en) 2013-09-19 2018-10-16 Siemens Aktiengesellschaft Combined cycle gas turbine plant comprising a waste heat steam generator and fuel preheating step
US11118781B2 (en) 2016-07-19 2021-09-14 Siemens Energy Global GmbH & Co. KG Vertical heat recovery steam generator

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Publication number Publication date
DE4321081A1 (de) 1995-01-05

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