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WO1994004795A1 - Procede de production d'energie dans une centrale thermique a gaz et a vapeur - Google Patents

Procede de production d'energie dans une centrale thermique a gaz et a vapeur Download PDF

Info

Publication number
WO1994004795A1
WO1994004795A1 PCT/DE1993/000741 DE9300741W WO9404795A1 WO 1994004795 A1 WO1994004795 A1 WO 1994004795A1 DE 9300741 W DE9300741 W DE 9300741W WO 9404795 A1 WO9404795 A1 WO 9404795A1
Authority
WO
WIPO (PCT)
Prior art keywords
steam
gas
gas turbine
fresh air
combustion chamber
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.)
Ceased
Application number
PCT/DE1993/000741
Other languages
German (de)
English (en)
Inventor
Gerhard Scholl
Lothar Stadie
Hans-Karl Petzel
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.)
Saarbergwerke AG
Siemens AG
Siemens Corp
Original Assignee
Saarbergwerke AG
Siemens AG
Siemens Corp
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 Saarbergwerke AG, Siemens AG, Siemens Corp filed Critical Saarbergwerke AG
Publication of WO1994004795A1 publication Critical patent/WO1994004795A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • 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
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • F01K21/042—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas pure steam being expanded in a motor somewhere in the plant
    • 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
    • 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
    • F02C3/305—Increasing the power, speed, torque or efficiency of a gas turbine or the thrust of a turbojet engine by injecting or adding water, steam or other fluids

Definitions

  • the invention relates to a method for generating energy in a combined gas-steam power plant with a gas turbine circuit in which fresh air is compressed and fed to a combustion chamber upstream of the gas turbine, and a steam turbine circuit with a preferably coal-fired steam generator.
  • the heat for the gas turbine cycle is generated by combustion of a gas, e.g. Natural gas or coal gasification gas, and the heat for the steam turbine cycle is obtained by burning coal in the steam generator.
  • a gas e.g. Natural gas or coal gasification gas
  • the residual heat still contained in the exhaust gas of the gas turbine is either fed directly to the steam turbine circuit via a waste heat boiler or it is used in that the exhaust gas of the gas turbine is introduced into the furnace of the steam generator with a still relatively high oxygen content.
  • the invention is therefore based on the object of reducing or completely avoiding the specific gas consumption of the gas turbine in a method of the type mentioned at the outset.
  • This object is achieved in that at least part of the compressed fresh air is preheated in the heat exchange with hot flue gas from the steam generator before entering the combustion chamber.
  • the fresh air is heated from the initial temperature of the air compressor from approximately 250 ° C. to approximately 800 ° C. If further heating to the inlet temperature of the gas turbine of, for example, 1150 ° C. is desired, this is then carried out in the combustion chamber of the gas turbine cycle.
  • the proposed measure means that the entire heat required in the gas turbine cycle, namely precisely the amount of heat required for heating to about 800 ° C., can be covered by the combustion of the throat in the steam generator, and that only the heat required for the further heating from 800 ⁇ C to about 1150 * C by burning a gas or oil must be applied in the combustion chamber of the gas turbine.
  • the invention thus makes it possible, when the gas turbine is in operation with an inlet temperature of approximately 800 ° C., to provide all of the heat required in the gas turbine cycle in the form of coal-derived heat.
  • the need for gas or oil in the combustion chamber of the gas turbine is greatly reduced.
  • the fresh air from the gas turbine cycle is mixed with steam from the steam cycle immediately before the heat exchange with the flue gas from the steam generator.
  • This measure leads to an additional increase in the efficiency of the overall system, since steam from the steam circuit of the steam turbine can now be expanded in a work-performing manner under the substantially higher temperature level of the gas turbine circuit in the gas turbine. Since the amount of fresh air to be compressed can also be reduced by an amount of air equivalent to the amount of steam added, the air compressor is greatly relieved. Basically, only the amount of air required for the combustion reactions in the combustion chamber during operation> 800 * C needs to be compressed, while the amount of working fluid additionally required for the operation of the gas turbine is available in the form of steam from the steam circuit of the steam turbine can be put. Since the steam is brought to pressure as condensate, the compression work to be performed for this only plays a subordinate role in comparison to the compression work saved in the air compressor of the gas turbine cycle.
  • the mass ratio to be set in each case of the water vapor or fresh air flows to be heated in the heat exchange with hot flue gas from the steam generator basically only depends on whether in the respective individual case either the lowest possible fuel consumption in the combustion chamber of the gas turbine or rather a possible one the highest possible efficiency of the entire system is sought.
  • a driving style is also conceivable that on the one hand with the highest efficiency, but on the other hand also with the highest fuel consumption in the combustion chamber of the gas turbine cycle is connected, in which only water vapor is heated in the heat exchange with the hot flue gas of the steam generator and is then introduced into the combustion chamber of the gas turbine cycle, while the fresh air compressed in the compressor of the gas turbine cycle is directly the Combustion chamber is fed.
  • already processed steam from the steam turbine circuit can also be introduced directly into the combustion chamber of the gas turbine circuit.
  • This process variant is e.g. of interest if, when retrofitting a power plant, the space available for the fresh air / flue gas heat exchanger to be installed in the steam generator is limited and it can therefore only be designed for the quantity of fresh air required in the combustion chamber of the gas turbine.
  • Another feature of the invention that is very important for the operation of the entire power plant provides for the exhaust gas of the gas turbine to be cooled with the fresh air for the steam generator in indirect heat exchange.
  • the residual heat of the gas turbine exhaust gas without the exhaust gas having to be introduced into the steam generator.
  • the residual oxygen content of the exhaust gas therefore no longer plays a role in the further treatment of the exhaust gas, so that the combustion chamber of the gas turbine can be operated almost stoichiometrically with respect to the combustion reactions, with the result that the nitrogen oxide formation is very low.
  • the heat exchange between the exhaust gas from the gas turbine and the fresh air for the steam generator can be set so that at least part of the water vapor contained in the exhaust gas is condensed in the course of the heat exchange. This means that at least part of the heat of vaporization released can be used again in the process. Further explanations of the invention can be found in the exemplary embodiment shown schematically in the figure.
  • the figure shows a combined gas-steam power plant with a gas turbine circuit with an air compressor 1, a combustion chamber 2, a gas turbine 3 and a generator 4 and a steam turbine circuit with a feed water pump 5, a coal-fired steam generator 6 with heating surfaces 7, 8, 9 and 10 for water heating, steam generation and steam superheating, a multi-stage steam turbine 11, a generator 12 and a condenser 13.
  • the fresh air required in the gas turbine cycle is fed to the compressor 1 via a line 14, compressed in the latter to approximately 12-15 bar and heated to approximately 280 ° C. in the process.
  • the fresh air flows according to the proposal according to the invention via a line 15 to additional heat exchanger surfaces 16 and 17 provided in the flue gas path of the steam generator 6, and is further heated in these to a temperature of about 800 * c in the heat exchange with hot flue gas.
  • the heated fresh air is then fed via a line 18 into the combustion chamber 2, in which part of the oxygen carried during operation is used at> 800 ° C. for the combustion of natural gas which flows in via a line 19 to the combustion chamber.
  • the exhaust gas from the combustion chamber is expanded at a temperature of approximately 800.degree. C. or 1150.degree.
  • the proposed routing of the fresh air over the heating surfaces 16 and 17 makes it possible, when the gas turbine is operating up to 800 ° C., to provide the entire amount of heat required for heating to the gas turbine inlet temperature via the steam generator 6.
  • the gas turbine is operated above 800 * C, the amount of natural gas required in the combustion chamber 2 is correspondingly greatly reduced.
  • the entire amount of fresh air from the compressor 1 is passed over the heating surfaces 16 and 17.
  • the condensate accumulating in the condenser 13 is pumped to the process pressure of about 300 bar in the feed water pump 5 and then heated, evaporated and superheated in the heating surfaces 7, 8, 9 and 10 of the steam generator 6.
  • the über ⁇ overheated steam leaves the steam generator 6 via a line 20 with a temperature to about 600 * C and is expanded to perform work in the Mat ⁇ stage formed steam turbine 11 and then recondensed in the condenser. 13
  • steam which has already largely been processed is drawn off from an intermediate stage of the steam turbine 11 at a temperature of about 350-400 ° C. and a pressure of about 17 bar via a line 21 and introduced into line 15.
  • the water vapor now passes through the heating surfaces 16 and 17 in a mixture with the fresh air compressed in the compressor 1 and is also heated therein to a temperature of about 800 ° C. Further heating to the inlet temperature> 800 * C of the gas turbine 3 then takes place in the combustion chamber 2.
  • this process feature makes it possible to relax some of the steam from the steam cycle under the high temperature of the gas turbine, while performing work.
  • the compressor 1 is greatly relieved, since basically only the amount of fresh air required for the combustion reactions in the combustion chamber needs to be compressed.
  • the additional amount of working fluid required for the gas turbine can be made available in the form of water vapor, which is pumped under pressure as condensate.
  • the optimal mixing ratio of fresh air and water vapor depends, among other things, on the design data of the entire system. However, it is also readily possible, for example in part-load operation, to drive the gas turbine exclusively with water vapor as the working medium. In this case, the fresh air compressor 1 can be switched off. be switched. It is also possible to supply the entire amount of fresh air compressed in the compressor 1 directly to the combustion chamber 2 and to heat only steam in the heating surfaces 16 and 17.
  • the resulting condensate is separated from the exhaust gas in a separator 24 and, after cleaning, can be fed back into the steam turbine circuit via a line 25.
  • the remaining exhaust gas is combined with the flue gas from the steam generator 6 cleaned in an electrostatic filter 26 and a flue gas desulfurization system 27 and then preferably discharged into the atmosphere via the cooling tower of the power plant, not shown here.

Landscapes

  • 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

Selon un procédé de production d'énergie dans une centrale thermique à gaz et à vapeur ayant un circuit de turbine à gaz, dans lequel l'air frais est comprimé et fourni à une chambre de combustion (2) montée en amont de la turbine à gaz (3), ainsi qu'un circuit de turbine à vapeur avec un générateur de vapeur (6) chauffé de préférence au charbon, au moins une partie de l'air frais comprimé est préchauffé (16, 17) par échange de chaleur avec le gaz de fumée chaud du générateur de vapeur (6) avant d'entrer dans la chambre de combustion (2). Ce procédé permet de couvrir une partie considérable des besoins thermiques du circuit de turbine à gaz par la chaleur en provenance de la combustion de charbon utilisée pour chauffer le générateur de vapeur. La consommation en huile ou en gaz dans le circuit de turbine à gaz est ainsi considérablement réduite.
PCT/DE1993/000741 1992-08-18 1993-08-17 Procede de production d'energie dans une centrale thermique a gaz et a vapeur Ceased WO1994004795A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19924227146 DE4227146A1 (de) 1992-08-18 1992-08-18 Verfahren zur Erzeugung von Energie in einer kombinierten Gas-Dampfkraftanlage
DEP4227146.0 1992-08-18

Publications (1)

Publication Number Publication Date
WO1994004795A1 true WO1994004795A1 (fr) 1994-03-03

Family

ID=6465697

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1993/000741 Ceased WO1994004795A1 (fr) 1992-08-18 1993-08-17 Procede de production d'energie dans une centrale thermique a gaz et a vapeur

Country Status (2)

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DE (1) DE4227146A1 (fr)
WO (1) WO1994004795A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1275821A1 (fr) * 2001-07-12 2003-01-15 Siemens Aktiengesellschaft Procédé pour le fonctionnment d'un groupe turbo à vapeur et centrale à vapeur pour mettre en oeuvre ce procèdè
DE10337240A1 (de) * 2003-08-13 2005-03-17 Siemens Ag Verfahren und Einrichtung zur Gewinnung von Wasser bei einer Kraftwerksanlage
US9404395B2 (en) * 2013-11-22 2016-08-02 Siemens Aktiengesellschaft Selective pressure kettle boiler for rotor air cooling applications
DE102018208026A1 (de) * 2018-05-22 2019-11-28 MTU Aero Engines AG Abgasbehandlungsvorrichtung, Flugzeugantriebssystem und Verfahren zum Behandeln eines Abgasstromes

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1312886A (fr) * 1961-07-13 1962-12-21 Siemens Ag Centrale thermique du type gaz-vapeur
DE2138664A1 (de) * 1971-07-23 1973-03-08 Sulzer Ag Verfahren zum gemischten gas- und dampfbetrieb einer gasturbinenanlage
DE3203082A1 (de) * 1982-01-30 1983-08-04 Rudolf Dr. 6800 Mannheim Wieser Kombinierte gasturbinen-dampfturbinenanlage bzw. kombinierte gasturbinen-dampferzeugeranlage
DE3815993A1 (de) * 1988-05-10 1989-11-23 Rudolf Dr Wieser Zweistoff-turbinenanlage
DE4019343A1 (de) * 1990-06-18 1991-12-19 Steinmueller Gmbh L & C Verfahren zur erzeugung elektrischer energie in einem kombi-kraftwerk und kombi-kraftwerk zur durchfuehruung des verfahrens

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2660680C1 (de) * 1976-10-27 1985-05-02 Joachim 4600 Dortmund Schwieger Verfahren zum Betreiben einer Gas-Dampfturbinenanlage
DE3613300A1 (de) * 1986-04-19 1987-10-22 Bbc Brown Boveri & Cie Verfahren zum erzeugen von elektrischer energie mit einer eine wirbelschichtfeuerung aufweisenden kombinierten gasturbinen-dampfkraftanlage sowie anlage zur durchfuehrung des verfahrens
DE3731082C1 (en) * 1987-09-16 1989-04-13 Steag Ag Method and plant for obtaining energy from solid, high-ballast fuels

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1312886A (fr) * 1961-07-13 1962-12-21 Siemens Ag Centrale thermique du type gaz-vapeur
DE2138664A1 (de) * 1971-07-23 1973-03-08 Sulzer Ag Verfahren zum gemischten gas- und dampfbetrieb einer gasturbinenanlage
DE3203082A1 (de) * 1982-01-30 1983-08-04 Rudolf Dr. 6800 Mannheim Wieser Kombinierte gasturbinen-dampfturbinenanlage bzw. kombinierte gasturbinen-dampferzeugeranlage
DE3815993A1 (de) * 1988-05-10 1989-11-23 Rudolf Dr Wieser Zweistoff-turbinenanlage
DE4019343A1 (de) * 1990-06-18 1991-12-19 Steinmueller Gmbh L & C Verfahren zur erzeugung elektrischer energie in einem kombi-kraftwerk und kombi-kraftwerk zur durchfuehruung des verfahrens

Also Published As

Publication number Publication date
DE4227146A1 (de) 1994-02-24

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