WO1999028608A1 - Preheating of intake air for gas turbine plants - Google Patents

Preheating of intake air for gas turbine plants Download PDF

Info

Publication number
WO1999028608A1
WO1999028608A1 PCT/DE1998/003478 DE9803478W WO9928608A1 WO 1999028608 A1 WO1999028608 A1 WO 1999028608A1 DE 9803478 W DE9803478 W DE 9803478W WO 9928608 A1 WO9928608 A1 WO 9928608A1
Authority
WO
WIPO (PCT)
Prior art keywords
gas turbine
air
gas
turbine system
steam
Prior art date
Application number
PCT/DE1998/003478
Other languages
German (de)
French (fr)
Inventor
Martin Krill
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 WO1999028608A1 publication Critical patent/WO1999028608A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • 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
    • F02C7/04—Air intakes for gas-turbine plants or jet-propulsion plants
    • F02C7/047—Heating to prevent icing
    • 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

Definitions

  • the invention relates to a gas turbine system in which intake air can be fed to the combustion chamber of a gas turbine. It further relates to a method for operating such a system. Furthermore, it relates to a gas and steam turbine system, which comprises a gas turbine system of the type mentioned above.
  • a gas turbine system is usually used to generate electrical energy.
  • the energy content of a fuel is used to generate a rotational movement of a turbine shaft, which in turn drives a generator or a work machine.
  • ambient air is usually sucked in and compressed to a high pressure in a valve assigned to the gas turbine.
  • Most of the compressed air enters one or more combustion chambers and is mixed there with the fuel, usually gas. Waste heat generated during operation of the gas turbine plant is usually dissipated into the environment.
  • a gas turbine system for example, a gas turbine system is known in which the air to be supplied to the combustion chamber is preheated by an air heater operated with hot exhaust gases.
  • DE 37 02 654 AI a gas and steam turbine plant is known, in which to directly preheat the intake air of the compressor unit, these hot exhaust gases are admixed from the boiler.
  • DE 41 37 946 AI in turn calls the use of steam emerging from a steam generator for preheating the combustion air which is fed to the combustion chamber.
  • the invention has for its object to provide a gas turbine system of the type mentioned above, which has a particularly high system efficiency.
  • a method for operating such a gas turbine system is to be specified, with which a particularly high system efficiency can be achieved.
  • intake air to be supplied to the compressor of a gas turbine can be preheated via heated exhaust air from an air-cooled generator, an exhaust air line of the air-cooled generator being divided into a first shut-off partial exhaust air line and a second shut-off partial exhaust air line branches, the first partial exhaust line opening into an intake air line upstream of the compressor of the gas turbine system.
  • the invention is based on the consideration that a particularly high -rue: i ⁇ iij> -.- '. Should be made available in the plant process waste heat to the maximum extent ⁇ "-k ngsgrad This should include the waste heat in the various Buildings of the gas turbine plant are produced, at least partially returned to the plant process, in which case it proves to be particularly advantageous if waste heat from an air-cooled generator reaches the intake house of the gas turbine in order to heat the air to be drawn in by the gas turbine.
  • the preheating of the intake air of the gas turbine By preheating the intake air of the gas turbine, the total mass flow of fuel-air mixture that can be supplied to the gas turbine per unit of time is reduced, so that the maximum output that can be achieved by the gas turbine is less than if the intake air is not preheated.
  • the preheating of the intake air causes the fuel consumption to drop more than the maximum achievable power output, so that the overall The efficiency of the system increases in this so-called partial load operation.
  • the gas turbine plant is particularly suitable for use in a gas and Dd.iLijjl ⁇ . j-iifci-.i dge gecigutL.
  • D ⁇ _j-- - ⁇ ⁇ ⁇ * ⁇ orte ⁇ lhafter- example be supplied to the compressor of the gas turbine intake air over m accumulating the Dampfturbmenstrom heated air from ⁇ a generator of Dampfturbmenstrom entnen bar. Because this use of waste heat enables a particularly high system efficiency of the gas and steam turbine plant in partial load operation by using the waste heat of the generator.
  • the waste heat of the generator ...-- Lc OiiJe-L ⁇ can be used in a cost-effective manner to provide a quick power reserve. This may also be necessary, for example, in the shortest response time to support the network frequencies in the power network fed by the gas and steam turbine system.
  • the waste heat generated by the Gerantor is only dissipated to the environment. This prevents preheating of the intake air for the gas turbine. This leads to a rapid increase in the maximum power delivered by the gas turbine.
  • the steam turbine system can be designed such that the heated exhaust air is only used in certain operating modes.
  • an exhaust air line advantageously has a branching into a first shut-off partial exhaust air line and into a second shut-off partial exhaust air line.
  • the first partial exhaust air line opens into an intake air line upstream of the compressor of the gas turbine system.
  • the stated object is achieved by preheating intake air to be supplied to the compressor of a gas turbine via heated exhaust air from an air-cooled generator.
  • this heat is used by the transfer of waste heat to the intake air for the gas turbine for the plant process of a gas uuibinenäniage ai -rj-. This also applies if this form of waste heat utilization is transferred to a gas and steam turbine plant.
  • the gas turbine system or the gas and steam turbine system thus has a particularly high system efficiency. Due to the comparatively slightly reduced maximum power output of the gas turbine, the efficiency is more favorable
  • such a gas turbine system or gas and steam turbine system also has comparatively lower pollutant emissions.
  • the so-called switchover point is relevant for the pollutant emissions of a gas turbine installation or a gas and steam turbine installation, which indicates the output at which the gas turbine is to be switched from diffusion operation to pre-operation.
  • the gas turbine system or the gas and steam turbine system with preheated intake air for the The gas turbine has a comparatively lower switchover point, so that it can be operated even in the case of comparatively low load conditions in the premix mode which is more favorable for low pollutant emissions.
  • FIG. 1 An embodiment of the invention is explained in more detail with reference to a drawing.
  • the figure schematically shows a gas turbine system which is integrated in a gas and steam turbine system.
  • the gas and steam turbine system 2 shown schematically in the figure comprises a gas turbine system 2a and a steam turbine system 2b.
  • the gas turbine plant 2a comprises a gas turbine 4 with a coupled air compressor 6.
  • the air compressor 6 is connected on the inlet side to an intake air line 8.
  • a gas chamber 4 is connected upstream of a combustion chamber 10, which is connected to a fresh air line 12 of the air compressor 6.
  • a fuel storage unit 14 opens into the combustion chamber 10 of the gas turbine 4. -.Li ⁇ i. ⁇ _; -> ran working medium AM from the combustion chamber 10 into the gas turbine 4, a line 15 is provided.
  • the gas turbine 4 and the air compressor 6 and a generator 16 are seated on a common shaft 18.
  • the steam turbine system 2b comprises a steam turbine 20 with a coupled generator 22.
  • the steam turbine system 2b also comprises a main condenser 26 which is placed in a water-steam circuit 24 of the steam turbine 20 and a heat recovery steam generator 28.
  • the steam turbine 20 consists of a first pressure stage or a High pressure part 20a and a second pressure stage or a medium pressure part 20b and a third pressure stage or a low pressure part 20c, which drive the generator 22 via a common shaft 30.
  • an exhaust gas line 32 is connected to an inlet 28a of the heat recovery steam generator. gers 28 connected.
  • the relaxed working medium AM 'from the steam turbine 4 leaves the heat recovery steam generator 28 via its outlet 28b in the direction of a comb (not shown in more detail).
  • the waste heat steam generator 28 comprises a high-pressure preheater or economizer 34, which is connected to a high-pressure drum 40 via a line 38 which can be shut off by a valve 36.
  • the high-pressure drum 40 is connected to a high-pressure evaporator 42 arranged in the waste heat steam generator 28 to form a water-steam circuit 44.
  • the high-pressure drum 40 is connected to a high-pressure superheater 46 which is arranged in the waste heat steam generator 28 and is connected on the outlet side to the steam inlet 48 of the high pressure part 20a of the steam turbine 20.
  • the Dampfa gga 50. ⁇ _- H uiuiucKtcj.! -. 2ü ⁇ _. r- ⁇ j ⁇ ) fturbine 20 is connected via a steam line 52 to an intermediate superheater 54 whose output 56 is connected via a steam line 58 to the steam inlet 60 of the medium-pressure part 20b of the steam turbine 20th
  • Its steam outlet 62 is connected via an overflow line 64 to the steam inlet 66 of the low-pressure part 20c of the steam turbine 20.
  • the steam outlet 68 of the low pressure part 20c of the steam turbine 20 is connected to the main condenser 26 via a steam line 70. This is about a 72, into which a feed water pump 74 is connected, connected to the economizer 34, so that a closed water-Da pf circuit 24 is formed.
  • heating surfaces are connected in a suitable manner to the steam inlet 60 of the medium pressure part 20b of the steam turbine 20 or to the steam inlet 66 of the low pressure part 20c of the steam turbine 20.
  • the gas and steam turbine system 2 is designed to achieve a particularly high degree of efficiency.
  • a first partial exhaust line 78a of the exhaust air line 78 of the generator 16 of the gas turbine system 2a opens into the intake air line 8 and can be shut off with a valve 76.
  • a second partial exhaust air line 78b, which can be shut off with a valve 80, of the exhaust air line 78 of the generator 16 of the gas turbine system 2a opens into the surroundings of the gas and steam turbine system 2.
  • the generator 22 of the steam turbine system 2b also has an exhaust air line 82, which is divided into a first one branched with a valve 84 partial exhaust line 82a and branched into a second partial exhaust line 82b which can be blocked with a valve 86.
  • the partial exhaust air _ • - .. -! _. l r 82a opens into the intake line o unu aie Ifc.-_ ic.j_- air line 82b opens into the surroundings of the gas and steam turbine system 2.
  • the intake air L to be supplied to the gas turbine 4 of the gas turbine system 2a can be preheated via waste heat A.
  • the waste heat A is heated waste air AL from the generator 16 of the gas turbine installation 2a and / or the generator 22 of the steam turbine installation 2b.
  • the heated exhaust air AL of the generator 16 of the gas turbine system 2a can be fed to the intake air line 8 of the air compressor 6 of the gas turbine system 2a via the shut-off partial exhaust line 78a.
  • the heated exhaust air from the generator 16 can also be discharged to the surroundings of the gas and steam turbine system 2 via a second shut-off partial flow line 78b.
  • the heated exhaust air AL of the generator 22 of the steam turbine system 2b of the intake air line 8 of the air compressor 6 of the gas turbine system 2a is likewise supplied via the shut-off partial exhaust air line 82a. bar.
  • the heated exhaust air of the generator 22 can also be supplied to the surroundings of the gas and steam turbine system 2 via the shut-off partial exhaust line 82b.
  • the gas and steam turbine system 2 By transferring the heated exhaust air AL, which either comes from the gas turbine system 2a and / or the steam turbine system 2b, to the intake air L for the gas turbine system 2a, this heat is returned to the energy conversion process of the gas and steam turbine system 2.
  • the gas and steam turbine system 2 thus has a particularly high system efficiency.
  • the preheating of the intake air L for the gas turbine system 2a also has the effect that the total mass flow of the working medium AM which can be supplied to the gas turbine 4 is lower than if the intake air L is not preheated.
  • the operation of the gas and steam turbine system 2 with preheating of the intake air L by heated exhaust air AL is therefore particularly suitable for the xeiiias r-et-riej. Zuciet .. is.
  • This mode of operation in a particularly simple form ensures a fast power reserve of the gas and steam turbine system 2. This is because if the preheating of the intake air L is switched off rapidly, the gas turbine 4 can rapidly increase the power output due to the then comparatively increased total mass flow of working medium AM that can be supplied.

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

In order to obtain a gas turbine plant (2a) with a particularly high efficiency, the intake air (L) to be supplied to the compressor (6) of a gas turbine (4) can be preheated by the outgoing air (AL) from an air-cooled generator (16).

Description

ANSAUGLUFTVORWARMUNG FÜR GASTURBINENANLAGEN INTAKE AIR PREHEATING FOR GAS TURBINE SYSTEMS
Die Erfindung bezieht sich auf eine Gasturbinenanlage, bei der der Brennkammer einer Gasturbine Ansaugluft zuführbar ist. Sie betrifft weiter ein Verfahren zum Betreiben einer derartigen Anlage. Weiterhin betrifft sie eine Gas- und Dampfturbinenanlage, die eine Gasturbinenanlage der oben genannten Art umfaßt.The invention relates to a gas turbine system in which intake air can be fed to the combustion chamber of a gas turbine. It further relates to a method for operating such a system. Furthermore, it relates to a gas and steam turbine system, which comprises a gas turbine system of the type mentioned above.
Eine Gasturbinenanlage wird üblicherweise zur Erzeugung elektrischer Energie eingesetzt. Dabei wird der Energieinhalt ei- nes Brennstoffes zur Erzeugung einer Rotationsbewegung einer Turbinenwelle genutzt, die wiederum einen Generator oder eine Arbeitsmaschine antreibt. Beim Betrieb der Gasturbinenanlage wird üblicherweise Umgebungsluft angesaugt und in einem der Gas urbine zugeordneten V.'-rc^X ter auf einen hohen Druck ver- dichtet. Der größte Anteil der verdichteten Luft gelangt in eine oder mehrere Brennkammern und wird dort mit dem Brennstoff, üblicherweise Gas, vermischt. Beim Betrieb der Gasturbinenanlage anfallende Abwärme wird üblicherweise in die Umgebung abgeführt.A gas turbine system is usually used to generate electrical energy. The energy content of a fuel is used to generate a rotational movement of a turbine shaft, which in turn drives a generator or a work machine. When the gas turbine system is in operation, ambient air is usually sucked in and compressed to a high pressure in a valve assigned to the gas turbine. Most of the compressed air enters one or more combustion chambers and is mixed there with the fuel, usually gas. Waste heat generated during operation of the gas turbine plant is usually dissipated into the environment.
Aus der DE 38 33 832 AI ist beispielsweise eine Gasturbinenanlage bekannt, bei der die der Brennkammer zuzuführende Luft durch einen mit heißen Abgasen betriebenen Lufterhitzer vorgewärmt wird. Aus der DE 37 02 654 AI hingegen ist eine Gas- und D.ampfturbinenanlage bekannt, bei der zur Vorwärmung der Ansaugluft der Verdichtereinheit dieser direkt heiße Abgase aus dem Kessel zugemischt werden. Die DE 41 37 946 AI wiederum nennt die Verwendung von aus einem Dampferzeuger austretendem Dampf zur Vorwärmung der Verbrennungsluft, die der Brennkammer zugeführt wird. Der Erfindung liegt die Aufgabe zugrunde, eine Gasturbinenanlage der oben genannten Art anzugeben, die einen besonders hohen Anlagenwirkungsgrad aufweist. Zudem soll ein Verfahren zum Betreiben einer derartigen Gasturbinenanlage angegeben werden, mit dem ein besonders hoher Anlagenwirkungsgrad erreichbar ist.From DE 38 33 832 AI, for example, a gas turbine system is known in which the air to be supplied to the combustion chamber is preheated by an air heater operated with hot exhaust gases. From DE 37 02 654 AI, however, a gas and steam turbine plant is known, in which to directly preheat the intake air of the compressor unit, these hot exhaust gases are admixed from the boiler. DE 41 37 946 AI in turn calls the use of steam emerging from a steam generator for preheating the combustion air which is fed to the combustion chamber. The invention has for its object to provide a gas turbine system of the type mentioned above, which has a particularly high system efficiency. In addition, a method for operating such a gas turbine system is to be specified, with which a particularly high system efficiency can be achieved.
Diese Aufgabe wird für eine Gasturbinenanlage der oben genannten Art erfindungsgemäß gelöst, indem dem Verdichter ei- ner Gasturbine zuzuführende Ansaugluft über erwärmte Abluft aus einem luftgekühlten Generator vorwärmbar ist, wobei sich eine Abluftleitung des luftgekühlten Generators in eine erste absperrbare Teilabluftleitung und in eine zweite absperrbare Teilabluftleitung verzweigt, wobei die erste Teilabluftlei- tung in eine dem Verdichter der Gasturbinenanlage vorgeschaltete Ansaugluftleitung mündet.This object is achieved according to the invention for a gas turbine system of the type mentioned above, in that intake air to be supplied to the compressor of a gas turbine can be preheated via heated exhaust air from an air-cooled generator, an exhaust air line of the air-cooled generator being divided into a first shut-off partial exhaust air line and a second shut-off partial exhaust air line branches, the first partial exhaust line opening into an intake air line upstream of the compressor of the gas turbine system.
Die Erfindung geht von der Überlegung aus, daß für einen besonders hohen -rü:iΞiij>-.- ':■ "-k ngsgrad im Anlagenprozeß anfallende Abwärme im größtmöglichen Umfang nutzbar gemacht werden sollte. Dabei sollte auch die Abwärme, die in den verschiedenen Gebäuden der Gasturbinenanlage anfällt, zumindest teilweise in den Anlagenprozeß rückgeführt werden. Hierbei erweist es sich als besonders günstig, wenn Abwärme aus einem luftgekühlten Generator vor das Ansaughaus der Gasturbine gelangt, um die von der Gasturbine anzusaugende Luft zu erwärmen.The invention is based on the consideration that a particularly high -rue: iΞiij> -.- '. Should be made available in the plant process waste heat to the maximum extent ■ "-k ngsgrad This should include the waste heat in the various Buildings of the gas turbine plant are produced, at least partially returned to the plant process, in which case it proves to be particularly advantageous if waste heat from an air-cooled generator reaches the intake house of the gas turbine in order to heat the air to be drawn in by the gas turbine.
Durch die Vorwärmung der Ansaugluft der Gasturbine verringert sich zwar der der Gasturbine insgesamt pro Zeiteinheit zuführbare Gesamtmassenstrom an Brennstoff-Luft-Gemisch, so daß die durch die Gasturbine maximal erreichbare Leistungsabgabe geringer ist als beim Verzicht auf die Vorwärmung der Ansaugluft. Wie sich allerdings herausgestellt hat, sinkt bei der Vorwärmung der Ansaugluft der Brennstoffverbrauch stärker als die maximal erreichbare Leistungsabgabe, so daß der Gesamt- Wirkungsgrad der Anlage m diesem sogenannten Teillastbetrieb steigt.By preheating the intake air of the gas turbine, the total mass flow of fuel-air mixture that can be supplied to the gas turbine per unit of time is reduced, so that the maximum output that can be achieved by the gas turbine is less than if the intake air is not preheated. However, as it turned out, the preheating of the intake air causes the fuel consumption to drop more than the maximum achievable power output, so that the overall The efficiency of the system increases in this so-called partial load operation.
Bei einem der Gasturbine zugeordneten Generator ist nun ubli- cherweise eine Abfuhrung der diesem zugefuhrten Kuhlluft über einen Kanal, der durch das Ansaughaus fuhrt, vorgesehen. Weist nun dieser Abluftkanal eine Verzweigung auf, über die die erwärmte Abluft entweder der Umgebung oder der Ansaugluft zuzuführen ist, so lassen sich mit besonders geringem Aufwand zwei verschiedene Betriebsarten einer Gasturbinenanlage bereitstellen. Bei Nutzung der erwärmten Abluft sollte die Anlage im Teillastbetrieb gefahren werden, denn dann steigt der Gesamtwirkungsgrad der Gasturbinenanlage. Ein Verzicht auf Nutzung der erwärmten Abluft sollte hingegen dann vorgesehen sein, wenn die maximale Leistungsabgabe der Gasturbinenanlage erreicht werden soll.In the case of a generator assigned to the gas turbine, a removal of the cooling air supplied to it is now usually provided via a duct that leads through the intake house. If this exhaust air duct now has a branch via which the heated exhaust air is to be supplied either to the environment or to the intake air, two different operating modes of a gas turbine system can be provided with particularly little effort. When using the heated exhaust air, the system should be operated in partial load operation, because then the overall efficiency of the gas turbine system increases. On the other hand, the use of the heated exhaust air should not be used if the maximum output of the gas turbine system is to be achieved.
Die Gasturbinenanlage ist besonders zum Einsatz m einer Gas- und Dd.iLijjl α. j-iifci-.i dge gecigutL. D<_j-- - ι~~ *τorteιlhafter- weise die dem Verdichter der Gasturbine zuzuführende Ansaugluft über m der Dampfturbmenanlage anfallende erwärmte Ab¬ luft eines Generators der Dampfturbmenanlage entnen bar . Denn diese Nutzung von Abwarme ermöglicht einen besonders hohen Anlagenwirkungsgrad der Gas- und Dampfturbmenanlage im Teillastbetrieb durch die Nutzung der Abwarme des Generators.The gas turbine plant is particularly suitable for use in a gas and Dd.iLijjl α. j-iifci-.i dge gecigutL. D <_j-- - ι ~ ~ * τ orteιlhafter- example be supplied to the compressor of the gas turbine intake air over m accumulating the Dampfturbmenanlage heated air from ¬ a generator of Dampfturbmenanlage entnen bar. Because this use of waste heat enables a particularly high system efficiency of the gas and steam turbine plant in partial load operation by using the waste heat of the generator.
In einer derartigen Anordnung ist die Abwarme des Generators ...-- Lc OiiJe-L≤ g nstiger Weise zur Bereitstellung einer schnellen Leistungsreserve nutzbar. Diese kann beispielsweise auch m kürzester Reaktionszeit zur Stutzung der Netzfrequenzen im von der Gas- und Dampfturbmenanlage bespeisten Stromnetz erforderlich sein. Zur Aktivierung der Leistungsreserve wird dabei die dem Gerantor anfallende Abwarme ausschließlich an die Umgebung abgeführt. Somit unterbleibt die Vorwarmung der Ansaugluft für die Gasturbine. Dies fuhrt zu einem raschen Anstieg der von der Gasturbine gelieferten Maximallei- stung. Die Dampfturbinenanlage kann derart ausgelegt sein, daß nur bei bestimmten Betriebsarten eine Nutzung der erwärmten Abluft vorgesehen ist. Hierfür weist eine Abluftleitung vorteilhafterweise eine Verzweigung in eine erste absperrbare Teilabluftleitung und in eine zweite absperrbare Teilabluftleitung auf. Hierbei mündet die erste Teilabluftleitung in eine dem Verdichter der Gasturbinenanlage vorgeschaltete Ansaugluftleitung.In such an arrangement, the waste heat of the generator ...-- Lc OiiJe-L≤ can be used in a cost-effective manner to provide a quick power reserve. This may also be necessary, for example, in the shortest response time to support the network frequencies in the power network fed by the gas and steam turbine system. To activate the power reserve, the waste heat generated by the Gerantor is only dissipated to the environment. This prevents preheating of the intake air for the gas turbine. This leads to a rapid increase in the maximum power delivered by the gas turbine. The steam turbine system can be designed such that the heated exhaust air is only used in certain operating modes. For this purpose, an exhaust air line advantageously has a branching into a first shut-off partial exhaust air line and into a second shut-off partial exhaust air line. Here, the first partial exhaust air line opens into an intake air line upstream of the compressor of the gas turbine system.
Bezüglich des Verfahrens zum Betreiben der Gasturbinenanlage oder der Gas- und Dampfturbinenanlage wird die genannte Aufgabe gelöst, indem dem Verdichter einer Gasturbine zuzuführende Ansaugluft über erwärmte Abluft aus einem luftgekühlten Generator vorgewärmt wird.With regard to the method for operating the gas turbine system or the gas and steam turbine system, the stated object is achieved by preheating intake air to be supplied to the compressor of a gas turbine via heated exhaust air from an air-cooled generator.
Die mit der Erfindung erzielten Vorteile bestehen insbesondere darin, daß durch die Übertragung von Abwärme auf die Ansaugluft für die Gasturbine diese Wärme für den Anlagenprozeß einer Gas uuibinenäniage nutz ai -rj- ht wird. Dies gilt auch dann, wenn diese Form der Abwärmenutzung auf eine Gas- und Dampfturbinenanlage übertragen wird. Die Gasturbinenanlage bzw. die Gas- und Dampfturbinenanlage weist somit einen besonders hohen Anlagenwirkungsgrad auf. Aufgrund der vergleichsweise geringfügig verminderten maximalen Leistungsab- gäbe der Gasturbine ist ein günstiger Wirkungsgrad derThe advantages achieved by the invention are, in particular, that this heat is used by the transfer of waste heat to the intake air for the gas turbine for the plant process of a gas uuibinenäniage ai -rj-. This also applies if this form of waste heat utilization is transferred to a gas and steam turbine plant. The gas turbine system or the gas and steam turbine system thus has a particularly high system efficiency. Due to the comparatively slightly reduced maximum power output of the gas turbine, the efficiency is more favorable
Gasturbinenanlage bzw. der Gas- und Dampfturbinenanlage ^ei besonders im Teillastbetrieb der Gasturbine erreichbar.Gas turbine system or the gas and steam turbine system ^ ei particularly accessible in partial load operation of the gas turbine.
Wie sich weiterhin herausgestellt hat, weist eine derartige Gasturbinenanlage bzw. Gas- und Dampfturbinenanlage auch vergleichsweise geringere Schadstoffemissionen auf. Neben anderen Größen ist für die Schadstoffemissionen einer Gasturbinenanlage bzw. einer Gas- und Dampfturbinenanlage der sogenannte Umschaltpunkt relevant, der angibt, bei welcher Lei— stung die Gasturbine vom Diffusionsbetrieb auf den Vor isch- betrieb umzustellen ist. Die Gasturbinenanlage bzw. die Gas- und Dampfturbinenanlage mit vorgewärmter Ansaugluft für die Gasturbine weist einen vergleichsweise niedrigeren Umschaltpunkt auf, so daß sie auch bei vergleichsweise niedrigen Lastzuständen im für geringe Schadstoffemissionen günstigeren Vormischbetrieb betreibbar ist.As has also been found, such a gas turbine system or gas and steam turbine system also has comparatively lower pollutant emissions. In addition to other variables, the so-called switchover point is relevant for the pollutant emissions of a gas turbine installation or a gas and steam turbine installation, which indicates the output at which the gas turbine is to be switched from diffusion operation to pre-operation. The gas turbine system or the gas and steam turbine system with preheated intake air for the The gas turbine has a comparatively lower switchover point, so that it can be operated even in the case of comparatively low load conditions in the premix mode which is more favorable for low pollutant emissions.
Ein Ausführungsbeispiel der Erfindung wird anhand einer Zeichnung näher erläutert. Darin zeigt die Figur schematisch eine Gasturbinenanlage, die in eine Gas- und Dampfturbinenanlage integriert ist.An embodiment of the invention is explained in more detail with reference to a drawing. The figure schematically shows a gas turbine system which is integrated in a gas and steam turbine system.
Die in der Figur schematisch dargestellte Gas- und Dampfturbinenanlage 2 umfaßt eine Gasturbinenanlage 2a und eine Dampfturbinenanlage 2b. Die Gasturbinenanlage 2a umfaßt eine Gasturbine 4 mit angekoppeltem Luftverdichter 6. Der Luftver- dichter 6 ist eingangsseitig an einer Ansaugluftleitung 8 angeschlossen. Der Gasturbine 4 ist eine Brennkammer 10 vorgeschaltet, die an eine Frischluftleitung 12 des Luftverdichters 6 angeschlossen ist. In die Brennkammer 10 der Gasturbine 4 mündet eine brennstorij-eituag 14.
Figure imgf000007_0001
-.Liώi.ι_;- >ran Ar- beitsmedium AM von der Brennkammer 10 in die Gasturbine 4 ist eine Leitung 15 vorgesehen. Die Gasturbine 4 und der Luftver- di nter 6 sowie ein Generator 16 sitzen auf einer gemeinsamen Welle 18.The gas and steam turbine system 2 shown schematically in the figure comprises a gas turbine system 2a and a steam turbine system 2b. The gas turbine plant 2a comprises a gas turbine 4 with a coupled air compressor 6. The air compressor 6 is connected on the inlet side to an intake air line 8. A gas chamber 4 is connected upstream of a combustion chamber 10, which is connected to a fresh air line 12 of the air compressor 6. A fuel storage unit 14 opens into the combustion chamber 10 of the gas turbine 4.
Figure imgf000007_0001
-.Liώi.ι _; -> ran working medium AM from the combustion chamber 10 into the gas turbine 4, a line 15 is provided. The gas turbine 4 and the air compressor 6 and a generator 16 are seated on a common shaft 18.
Die Dampfturbinenanlage 2b umfaßt eine Dampfturbine 20 mit angekoppeltem Generator 22. Die Dampfturbinenanlage 2b umfaßt außerdem einen in einem Wasser-Dampf-Kreislauf 24 der Dampfturbine 20 nac geschaϊteten Hauptkcndensator 26 sowie einen Abhitzedampferzeuger 28. Die Dampfturbine 20 besteht aus ei- ner ersten Druckstufe oder einem Hochdruckteil 20a und einer zweiten Druckstufe oder einem Mitteldruckteil 20b sowie einer dritten Druckstufe oder einem Niederdruckteil 20c, die über eine gemeinsame Welle 30 den Generator 22 antreiben.The steam turbine system 2b comprises a steam turbine 20 with a coupled generator 22. The steam turbine system 2b also comprises a main condenser 26 which is placed in a water-steam circuit 24 of the steam turbine 20 and a heat recovery steam generator 28. The steam turbine 20 consists of a first pressure stage or a High pressure part 20a and a second pressure stage or a medium pressure part 20b and a third pressure stage or a low pressure part 20c, which drive the generator 22 via a common shaft 30.
Zum Zuführen von in der Gasturbine 4 entspanntem Arbeitsmittel AM' oder Rauchgas in den Abhitzedampferzeuger 28 ist eine Abgasleitung 32 an einen Eingang 28a des Abhitzedampferzeu- gers 28 angeschlossen. Das entspannte Arbeitsmittel AM' aus der Dampfturbine 4 verlaßt den Abhitzedampferzeuger 28 über dessen Ausgang 28b in Richtung auf einen nicht naher dargestellten Kamm.In order to supply working medium AM ′ or flue gas relaxed in the gas turbine 4 into the heat recovery steam generator 28, an exhaust gas line 32 is connected to an inlet 28a of the heat recovery steam generator. gers 28 connected. The relaxed working medium AM 'from the steam turbine 4 leaves the heat recovery steam generator 28 via its outlet 28b in the direction of a comb (not shown in more detail).
Der Abhitzedampferzeuger 28 umfaßt m einer ersten Druckstufe oder Hochdruckstufe des Wasser-Dampf-Kreislaufs 24 einen Hochdruckvorwarmer oder Economizer 34, der über eine mit einem Ventil 36 absperrbare Leitung 38 an eine Hochdrucktrom- mel 40 angeschlossen ist. Die Hochdrucktrommel 40 ist mit einem im Abhitzedampferzeuger 28 angeordneten Hochdruckverdampfer 42 zur Bildung eines Wasser-Dampf-Umlaufs 44 verbunden. Zum Abfuhren von Frischdampf F ist die Hochdrucktrommel 40 an einen im Abhitzedampferzeuger 28 angeordneten Hochdruckuber- hitzer 46 angeschlossen, der ausgangsseitig mit dem Dampfeinlaß 48 des Hochdruckteils 20a der Dampfturbine 20 verbunden ist.In a first pressure stage or high-pressure stage of the water-steam circuit 24, the waste heat steam generator 28 comprises a high-pressure preheater or economizer 34, which is connected to a high-pressure drum 40 via a line 38 which can be shut off by a valve 36. The high-pressure drum 40 is connected to a high-pressure evaporator 42 arranged in the waste heat steam generator 28 to form a water-steam circuit 44. To remove live steam F, the high-pressure drum 40 is connected to a high-pressure superheater 46 which is arranged in the waste heat steam generator 28 and is connected on the outlet side to the steam inlet 48 of the high pressure part 20a of the steam turbine 20.
Der Dampfa üla 50 .^_- H uiuiucKtcj.!-. 2üα _. r-jτ~)fturbine 20 ist über eine Dampfleitung 52 mit einem Zwischenuberhitzer 54 verbunden, dessen Ausgang 56 über eine Dampfleitung 58 an den Dampfeinlaß 60 des Mitteldruckteils 20b der Dampfturbine 20 angeschlossen ist. Dessen Dampfauslaß 62 ist über eine Überströmleitung 64 mit dem Dampfeinlaß 66 des Niederdruck- teils 20c der Dampfturbine 20 verbunden. Der Dampfauslaß 68 des Niederdruckteils 20c der Dampfturbine 20 ist über eine Dampfleitung 70 an den Hauptkondensator 26 angeschlossen. Diesei i.t über eine
Figure imgf000008_0001
72, in die eine Speisewasserpumpe 74 geschaltet ist, mit dem Economizer 34 verbunden, so daß ein geschlossener Wasser-Da pf-Kreislauf 24 entsteht.The Dampfa üla 50. ^ _- H uiuiucKtcj.! -. 2üα _. r- ~ j τ) fturbine 20 is connected via a steam line 52 to an intermediate superheater 54 whose output 56 is connected via a steam line 58 to the steam inlet 60 of the medium-pressure part 20b of the steam turbine 20th Its steam outlet 62 is connected via an overflow line 64 to the steam inlet 66 of the low-pressure part 20c of the steam turbine 20. The steam outlet 68 of the low pressure part 20c of the steam turbine 20 is connected to the main condenser 26 via a steam line 70. This is about a
Figure imgf000008_0001
72, into which a feed water pump 74 is connected, connected to the economizer 34, so that a closed water-Da pf circuit 24 is formed.
In dem Ausfuhrungsbeispiel gemäß der Figur ist somit lediglich die erste Druckstufe des Wasser-Dampf-Kreislaufs 24 de- tailliert dargestellt. Im Abhitzedampferzeuger 28 können jedoch noch weitere, nicht näher dargestellte Heizflachen angeordnet sein, die jeweils einer Mittel- oder einer Nieder- druckstufe des Wasser-Dampf-Kreislaufs 24 zugeordnet sind. Diese Heizflächen sind in geeigneter Weise mit dem Dampfeinlaß 60 des Mitteldruckteils 20b der Dampfturbine 20 oder mit dem Dampfeinlaß 66 des Niederdruckteils 20c der Dampftur- bine 20 verbunden.In the exemplary embodiment according to the figure, only the first pressure stage of the water-steam circuit 24 is shown in detail. In the heat recovery steam generator 28, however, further heating surfaces, not shown, can be arranged, each of which has a medium or a low Pressure level of the water-steam circuit 24 are assigned. These heating surfaces are connected in a suitable manner to the steam inlet 60 of the medium pressure part 20b of the steam turbine 20 or to the steam inlet 66 of the low pressure part 20c of the steam turbine 20.
Die Gas- und Dampfturbinenanlage 2 ist zur Erzielung eines besonders hohen Wirkungsgrades ausgelegt. Dazu mündet in die Ansaugluftleitung 8 eine erste, mit einem Ventil 76 absperr- bare Teilabluftleitung 78a der Abluftleitung 78 des Generators 16 der Gasturbinenanlage 2a. Eine zweite, mit einem Ventil 80 absperrbare Teilabluftleitung 78b der Abluftleitung 78 des Generators 16 der Gasturbinenanlage 2a mündet in die Umgebung der Gas- und Dampfturbinenanlage 2. Auch der Genera- tor 22 der Dampfturbinenanlage 2b weist eine Abluftleitung 82 auf, die sich in eine erste, mit einem Ventil 84 absperrbare Teilabluftleitung 82a und in eine zweite, mit einem Ventil 86 absperrbare Teilabluftleitung 82b verzweigt. Die Teilabluft- _ •-..-!_. lr 82a mündet in die Ansaugiurtleitung o unu αie Ifc.-_ic.j_- luftleitung 82b mündet in die Umgebung der Gas- und Dampfturbinenanlage 2.The gas and steam turbine system 2 is designed to achieve a particularly high degree of efficiency. For this purpose, a first partial exhaust line 78a of the exhaust air line 78 of the generator 16 of the gas turbine system 2a opens into the intake air line 8 and can be shut off with a valve 76. A second partial exhaust air line 78b, which can be shut off with a valve 80, of the exhaust air line 78 of the generator 16 of the gas turbine system 2a opens into the surroundings of the gas and steam turbine system 2. The generator 22 of the steam turbine system 2b also has an exhaust air line 82, which is divided into a first one branched with a valve 84 partial exhaust line 82a and branched into a second partial exhaust line 82b which can be blocked with a valve 86. The partial exhaust air _ • - .. -! _. l r 82a opens into the intake line o unu aie Ifc.-_ ic.j_- air line 82b opens into the surroundings of the gas and steam turbine system 2.
Bei der Gas- und Dampfturbinenanlage 2 ist die der Gasturbine 4 der Gasturbinenanlage 2a zuzuführende Ansaugluft L über Abwärme A vorwärmbar. Bei der Abwärme A handelt es sich um erwärmte Abluft AL des Generators 16 der Gasturbinenanlage 2a und/oder des Generators 22 der Dampfturbinenanlage 2b. Die erwärmte Abluft AL des Generators 16 der Gasturbinenanlage 2a ist der Ansaugluftleitung 8 des Luftverdich- ters 6 der Gasturbinenanlage 2a über die absperrbare Teilab- luftleitung 78a zuführbar. Alternativ kann die erwärmte Abluft des Generators 16 aber auch über eine zweite absperrbare Teilstromleitung 78b an die Umgebung der Gas- und Dampfturbinenanlage 2 abgeführt werden. Über die absperrbare Teilab- luftleitung 82a ist ebenfalls die erwärmte Abluft AL des Generators 22 der Dampfturbinenanlage 2b der Ansaugluftleitung 8 des Luftverdichters 6 der Gasturbinenanlage 2a zuführ- bar. Alternativ kann die erwärmte Abluft des Generators 22 aber auch der Umgebung der Gas- und Dampfturbinenanlage 2 über die absperrbare Teilabluftleitung 82b zugeführt werden.In the gas and steam turbine system 2, the intake air L to be supplied to the gas turbine 4 of the gas turbine system 2a can be preheated via waste heat A. The waste heat A is heated waste air AL from the generator 16 of the gas turbine installation 2a and / or the generator 22 of the steam turbine installation 2b. The heated exhaust air AL of the generator 16 of the gas turbine system 2a can be fed to the intake air line 8 of the air compressor 6 of the gas turbine system 2a via the shut-off partial exhaust line 78a. Alternatively, the heated exhaust air from the generator 16 can also be discharged to the surroundings of the gas and steam turbine system 2 via a second shut-off partial flow line 78b. The heated exhaust air AL of the generator 22 of the steam turbine system 2b of the intake air line 8 of the air compressor 6 of the gas turbine system 2a is likewise supplied via the shut-off partial exhaust air line 82a. bar. Alternatively, the heated exhaust air of the generator 22 can also be supplied to the surroundings of the gas and steam turbine system 2 via the shut-off partial exhaust line 82b.
Durch die Übertragung der erwärmten Abluft AL, die entweder aus der Gasturbinenanlage 2a und/oder der Dampfturbinenanlage 2b stammt, auf die Ansaugluft L für die Gasturbinenanlage 2a wird diese Wärme in den Energieumwandlungsprozeß der Gas- und Dampfturbinenanlage 2 zurückgeführt. Die Gas- und Dampfturbinenanlage 2 weist somit einen besonders hohen Anlagenwirkungsgrad auf. Andererseits bewirkt die Vorwärmung der Ansaugluft L für die Gasturbinenanlage 2a aber auch, daß der Gesamtmassenstrom des der Gasturbine 4 zuführbaren Arbeitsmediums AM geringer ist als beim Verzicht auf die Vorwärmung der Ansaugluft L. Die bei Betrieb der Gasturbine 4 erreichbare maximale Leistungsabgabe ist somit vergleichsweise geringer. Der Betrieb der Gas- und Dampfturbinenanlage 2 mit Vorwärmung der Ansaugluft L durch erwärmte Abluft AL eignet s Xh somit besonders für den xeiiias r-et-riej . Zuciet.. is. i--^- dieser Betriebsart in besonders einfacher Form eine schnelle Leistungsreserve der Gas- und Dampfturbinenanlage 2 gewährleistet. Denn bei einer Schnellabschaltung der Vorwärmung der Ansaugluft L ist aufgrund des dann vergleichsweise erhöhten lieferbaren Gesamtmassenstroms an Arbeitsmedium AM für die Gasturbine 4 eine rasche Erhöhung der Leistungsabgabe der Gasturbine 4 möglich. By transferring the heated exhaust air AL, which either comes from the gas turbine system 2a and / or the steam turbine system 2b, to the intake air L for the gas turbine system 2a, this heat is returned to the energy conversion process of the gas and steam turbine system 2. The gas and steam turbine system 2 thus has a particularly high system efficiency. On the other hand, the preheating of the intake air L for the gas turbine system 2a also has the effect that the total mass flow of the working medium AM which can be supplied to the gas turbine 4 is lower than if the intake air L is not preheated. The operation of the gas and steam turbine system 2 with preheating of the intake air L by heated exhaust air AL is therefore particularly suitable for the xeiiias r-et-riej. Zuciet .. is. i - ^ - This mode of operation in a particularly simple form ensures a fast power reserve of the gas and steam turbine system 2. This is because if the preheating of the intake air L is switched off rapidly, the gas turbine 4 can rapidly increase the power output due to the then comparatively increased total mass flow of working medium AM that can be supplied.

Claims

Patentansprüche claims
1. Gasturbinenanlage (2a), bei der dem Verdichter (6) einer Gasturbine (4) zuzuführende Ansaugluft (L) über erwärmte Ab- luft (AL) aus einem luftgekühlten Generator (16) vorwärmbar ist, wobei sich eine Abluftleitung (78) des luftgekühlten Generators (16) in eine erste absperrbare Teilabluftleitung (78a) und in eine zweite absperrbare Teilabluftleitung (78b) verzweigt, wobei die erste Teilabluftleitung (78a) in eine dem Verdichter (6) der Gasturbinenanlage (2a) vorgeschaltete -Ansaugluftleitung (8) mündet.1. Gas turbine system (2a), in which intake air (L) to be supplied to the compressor (6) of a gas turbine (4) can be preheated via heated exhaust air (AL) from an air-cooled generator (16), an exhaust air line (78) of the Air-cooled generator (16) branches into a first shut-off partial exhaust line (78a) and a second shut-off partial exhaust line (78b), the first partial exhaust line (78a) opening into an intake air line (8) upstream of the compressor (6) of the gas turbine system (2a) .
2. Gas- und Dampfturbinenanlage (2) mit einem einer Gasturbine (4) rauchgasseitig nachgeschalteten Abhitzedampferzeu- ger (28), dessen Heizflächen in den Wasser-Dampf-Kreislauf (24) einer Dampfturbine (20) geschaltet sind, wobei dem Verdichter (6) der Gasturbine (4) zuzuführende Ansaugluft (AL) über in der Dampfturbinenanlage (2b) anfallende er- '. r r X"- 'i ^ X ~ eines luftgekühlten Generators (.-..-,, cie-- Dampfturbinenanlage vorwärmbar ist, wobei sich eine Abluftleitung (82) in eine erste absperrbare Teilabluftleitung (82a) und in eine zweit--, absperrbare Teilabluftleitung (82b) verzweigt, wobei die erste Teilabluftleitung (82a) in eine dem Verdichter (6) der Gasturbinenanlage (2a) vorge- schaltete Ansaugluftleitung (8) mündet.2. Gas and steam turbine system (2) with a waste heat steam generator (28) connected downstream of a gas turbine (4) on the flue gas side, the heating surfaces of which are connected to the water-steam circuit (24) of a steam turbine (20), the compressor (6 ) of the intake gas (AL) to be supplied to the gas turbine (4) via the air generated in the steam turbine system (2b). rr X " - 'i ^ X ~ of an air-cooled generator (.-..- ,, cie-- steam turbine plant can be preheated, with an exhaust air line (82) in a first blockable partial exhaust line (82a) and in a second, blockable Partial exhaust air line (82b) branches, the first partial exhaust air line (82a) opening into an intake air line (8) connected upstream of the compressor (6) of the gas turbine system (2a).
3. Gas- und Dampfturbinenanlage (2) nach Anspruch 2, die eine Gasturbinenanlage (2a) nach Anspruch 1 aufweist.3. Gas and steam turbine system (2) according to claim 2, which has a gas turbine system (2a) according to claim 1.
4. Verfahren zum Betreiben einer Gasturbinenanlage (2a) nach Anspruch 1, bei dem dem Verdichter (6) einer Gasturbine (4) zuzuführende Ansaugluft (L) über in der Gasturbinenanlage (2a) anfallende erwärmte Abluft (AL) aus einem luftgekühlten Generator (16) vorgewärmt wird.4. The method for operating a gas turbine system (2a) according to claim 1, in which the compressor (6) of a gas turbine (4) intake air (L) to be generated in the gas turbine system (2a) from the heated exhaust air (AL) from an air-cooled generator (16 ) is preheated.
5. Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage (2) nach Anspruch 2 oder 3, bei dem dem Verdichter (6; einer Gasturbine (4) zuzuführende Ansaugluft (AL) über in der Dampfturbinen- und/oder der Gasturbinenanlage (2a, 2b) anfallende erwärmte Abluft (AL) aus einem luftgekühlten Generator (16) vorgewärmt wird. 5. A method of operating a gas and steam turbine system (2) according to claim 2 or 3, in which the compressor (6; Intake air (AL) to be supplied to a gas turbine (4) is preheated from an air-cooled generator (16) via heated exhaust air (AL) generated in the steam turbine and / or the gas turbine system (2a, 2b).
PCT/DE1998/003478 1997-12-01 1998-11-25 Preheating of intake air for gas turbine plants WO1999028608A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1997153264 DE19753264C1 (en) 1997-12-01 1997-12-01 Gas turbine plant and method for operating a gas turbine plant and gas and steam turbine plant
DE19753264.0 1997-12-01

Publications (1)

Publication Number Publication Date
WO1999028608A1 true WO1999028608A1 (en) 1999-06-10

Family

ID=7850403

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1998/003478 WO1999028608A1 (en) 1997-12-01 1998-11-25 Preheating of intake air for gas turbine plants

Country Status (2)

Country Link
DE (1) DE19753264C1 (en)
WO (1) WO1999028608A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2500454A (en) * 2012-03-21 2013-09-25 Mitsui Shipbuilding Eng Gas turbine intake anti-icing device
CN105705735A (en) * 2013-11-05 2016-06-22 西门子公司 Thermal power plant with use of the waste heat from a generator

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2196633A1 (en) * 2008-12-15 2010-06-16 Siemens Aktiengesellschaft Power plant with a turbine unit and a generator

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2508397A (en) * 1948-12-14 1950-05-23 Kane Saul Allan Cooling means for gas turbogenerators
DE865842C (en) * 1945-04-13 1953-02-05 Siemens Ag Constant pressure gas turbine engine set
DE1751613A1 (en) * 1968-06-28 1971-04-29 Klaue Hermann Electric generator driven by a combustion turbine, especially for vehicle drives
DE3002615A1 (en) * 1979-12-05 1981-06-11 BBC AG Brown, Boveri & Cie., Baden, Aargau Combined gas and steam turbine power plant - uses gas turbine waste heat to generate steam, preheats air-to-gas turbine compressor
DE3702654A1 (en) 1986-02-07 1987-08-13 Westinghouse Electric Corp METHOD FOR OPERATING A GAS TURBINE PLANT WITH LOW-VALUE FUEL
DE3833832A1 (en) 1988-10-05 1990-04-12 Krantz Gmbh Energieplanung H Method for the operation of a thermal power plant
DE4137946A1 (en) 1991-11-18 1993-05-19 Siemens Ag Gas and steam power plant - incorporates gas turbine whose exhaust gas heat is used for steam prodn. and steam is fed to steam turbine and heat exchanger
DE19622057A1 (en) * 1996-05-31 1997-12-04 Energieversorgung Halle Gmbh Method and device for the efficient use of waste heat in power engines

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE865842C (en) * 1945-04-13 1953-02-05 Siemens Ag Constant pressure gas turbine engine set
US2508397A (en) * 1948-12-14 1950-05-23 Kane Saul Allan Cooling means for gas turbogenerators
DE1751613A1 (en) * 1968-06-28 1971-04-29 Klaue Hermann Electric generator driven by a combustion turbine, especially for vehicle drives
DE3002615A1 (en) * 1979-12-05 1981-06-11 BBC AG Brown, Boveri & Cie., Baden, Aargau Combined gas and steam turbine power plant - uses gas turbine waste heat to generate steam, preheats air-to-gas turbine compressor
DE3702654A1 (en) 1986-02-07 1987-08-13 Westinghouse Electric Corp METHOD FOR OPERATING A GAS TURBINE PLANT WITH LOW-VALUE FUEL
DE3833832A1 (en) 1988-10-05 1990-04-12 Krantz Gmbh Energieplanung H Method for the operation of a thermal power plant
DE4137946A1 (en) 1991-11-18 1993-05-19 Siemens Ag Gas and steam power plant - incorporates gas turbine whose exhaust gas heat is used for steam prodn. and steam is fed to steam turbine and heat exchanger
DE19622057A1 (en) * 1996-05-31 1997-12-04 Energieversorgung Halle Gmbh Method and device for the efficient use of waste heat in power engines

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2500454A (en) * 2012-03-21 2013-09-25 Mitsui Shipbuilding Eng Gas turbine intake anti-icing device
JP2013194619A (en) * 2012-03-21 2013-09-30 Mitsui Eng & Shipbuild Co Ltd Gas turbine intake anti-icing device
CN105705735A (en) * 2013-11-05 2016-06-22 西门子公司 Thermal power plant with use of the waste heat from a generator

Also Published As

Publication number Publication date
DE19753264C1 (en) 1999-06-17

Similar Documents

Publication Publication Date Title
EP1023526B1 (en) Gas and steam turbine installation and method for operating an installation of this type
EP0150340B1 (en) Method of operating a combined gas/steam turbine power plant
EP0523467B1 (en) Method of operating a gas and steam turbines plant and plant for carrying out the method
EP0819209B1 (en) Method of operating a waste-heat steam generator, and a waste-heat steam generator operated by this method
EP0783619B1 (en) Method of operating a gas and steam turbine plant
EP0591163B1 (en) Combined gas and steam turbine plant
EP0674099A1 (en) Cooling method for the thermically charged components of a gasturbine powerplant
DE69930026T2 (en) Combined cycle power plant
CH678987A5 (en)
EP1119688A1 (en) Gas and steam turbine installation
DE102018123663A1 (en) Fuel preheating system for a combustion gas turbine
DE102014111152A1 (en) Channel ignited combination cycle system
EP1105624B1 (en) Gas and steam turbine unit
DE3002615A1 (en) Combined gas and steam turbine power plant - uses gas turbine waste heat to generate steam, preheats air-to-gas turbine compressor
DE102010016548A1 (en) System and method for fuel heating for a gas turbine
DE69812811T2 (en) Method and arrangement for combined cycle power plants
EP0220510B1 (en) Pressurized combustor for a steam generator
EP1286030B1 (en) Gas and air turbine powerplant
EP0981681B1 (en) Gas and steam turbine system, and refrigeration of the coolant intended for the gas turbine in such a system
WO1999028608A1 (en) Preheating of intake air for gas turbine plants
EP0868599B1 (en) Process for operating a gas turbine and gas turbine operating in this way
EP3810907B1 (en) Exhaust gas recirculation in gas and steam turbines plants
WO1995025880A1 (en) Process for operating a waste heat steam generator and waste heat steam generator so operated
EP1404947B1 (en) Method for operating a steam power plant and steam power plant for carrying out said method
EP1242729B1 (en) Method for operating a steam turbine, and a turbine system provided with a steam turbine that functions according to said method

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): CN ID JP KR RU UA US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE

121 Ep: the epo has been informed by wipo that ep was designated in this application
122 Ep: pct application non-entry in european phase