EP1023526B1 - Gas- und dampfturbinenanlage und verfahren zum betreiben einer derartigen anlage - Google Patents

Gas- und dampfturbinenanlage und verfahren zum betreiben einer derartigen anlage Download PDF

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Publication number
EP1023526B1
EP1023526B1 EP98958189A EP98958189A EP1023526B1 EP 1023526 B1 EP1023526 B1 EP 1023526B1 EP 98958189 A EP98958189 A EP 98958189A EP 98958189 A EP98958189 A EP 98958189A EP 1023526 B1 EP1023526 B1 EP 1023526B1
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EP
European Patent Office
Prior art keywords
steam
gas
turbine
condenser
steam turbine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98958189A
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German (de)
English (en)
French (fr)
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EP1023526A1 (de
Inventor
Martin Krill
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Siemens AG
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Siemens AG
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Publication of EP1023526B1 publication Critical patent/EP1023526B1/de
Anticipated expiration legal-status Critical
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    • 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

Definitions

  • the invention relates to a gas and steam turbine plant with a gas turbine downstream of a gas turbine Heat recovery steam generator, its heating surfaces in the water-steam cycle a steam turbine are switched. It affects further a method for operating such Gas and steam turbine plant.
  • the heat transfer takes place in one of the gas turbines on the flue gas side downstream heat recovery steam generator, in the heating surfaces are arranged in the form of tubes or tube bundles. These in turn are in the water-steam cycle of the steam turbine connected.
  • the water-steam cycle typically includes several, for example two, pressure stages, wherein a preheating and an evaporator heating surface for each pressure level having.
  • the steam generated in the waste heat steam generator becomes the steam turbine fed where he relaxes while working.
  • the Steam turbine can include a number of pressure levels, the number and design of the design of the heat recovery steam generator are adjusted.
  • the one relaxed in the steam turbine Steam is usually fed to a condenser and condenses there. That with the condensation of the steam
  • the resulting condensate is used as feed water for the waste heat steam generator fed again, so that a closed water-steam cycle arises.
  • the condenser of such a gas and steam turbine plant is usually in the form of a heat exchanger with a Coolant acted upon, which is the steam for condensation Removes heat.
  • Water is usually used as the cooling medium intended; alternatively, the capacitor can also be used as a Air condenser charged with air as the cooling medium his.
  • the invention has for its object a gas and Steam turbine system of the type mentioned above, which also a particularly high one in different operating states System efficiency.
  • a process for Operating such a gas and steam turbine plant be specified with a particularly high Plant efficiency is achievable.
  • This task is for a gas and steam turbine plant Solved above type according to the invention by one of the Steam turbine-associated main condenser on the water-steam side another capacitor is connected in parallel, which over the intake air to be supplied to the gas turbine can be cooled.
  • the invention is based on the consideration that for a particular high system efficiency in the system process Heat should be used to the greatest extent possible.
  • the steam extracted during its condensation should also be removed Heat - at least in part - in the plant process be returned. Due to the temperature level of the steam at its condensation of about 60 ° C is the transfer the heat extracted in the process of supplying the gas turbine Intake air particularly cheap.
  • the capacitor can be in the manner of an additional capacitor be tapped with steam from the steam turbine.
  • the capacitor is special inexpensive way to provide a quick performance reserve usable, for example, in shorter Response time to support the grid frequency in the gas and Steam turbine system powered electricity grid required can be. It is used to activate the power reserve the steam supply to the condenser is interrupted, so that the entire Steam flow is carried over the main condenser. Consequently there is no preheating of the intake air for the gas turbine, resulting in a rapid increase in the amount supplied by the gas turbine Maximum performance leads.
  • a compressor is usually assigned to the gas turbine, where the intake air for the gas turbine via an intake air line is feedable.
  • the Condenser on the coolant side directly into this intake air line connected is expediently designed as an air condenser, being due to the single-stage heat transfer from the condensing Steam on the intake air losses due to Conversion processes are kept particularly low.
  • the capacitor to the coolant side via an intermediate cooling circuit Heat exchanger connected, which in turn on the secondary side into the intake air line upstream of the gas turbine is.
  • the steam ratio between the condenser and Steam streams to be fed to the main condenser is expedient adjustable, preferably depending on Load state of the gas and steam turbine plant.
  • the one about the Main condenser-led steam flow is used when operating a such system in the usual way using a external coolant condenses. Due to the adjustability the steam quantity ratio between the steam flows the operating parameters of the capacitor Steam flow almost constant in a particularly simple manner are kept, so that such a system particularly is reliably operable. It is also for everyone Operating state of the system to the intake air for the particular Operating state maximum achievable temperature preheatable.
  • the main condenser is expediently a condensate preheater downstream, with outflowing from the condenser Condensate seen in the direction of flow of the condensate after the condensate preheater into the water-steam cycle the steam turbine can be fed. So after the Condensation of the steam residual heat remaining in the condensate in a particularly favorable way in the water-steam cycle recoverable.
  • the condensate obtained in the condensation is advantageously in the water-steam cycle of the steam turbine pre-warmed condensate.
  • the advantages achieved with the invention are in particular in that by the transfer of condensation the heat extracted from the steam to the intake air for the Gas turbine made this heat usable for the plant process becomes.
  • Such a gas and steam turbine system thus has a particularly high level of system efficiency. Due to the comparatively slightly reduced maximum power output the gas turbine is a favorable efficiency of the gas and Steam turbine, particularly in the partial load range Gas turbine accessible.
  • Gas and steam turbine plant also comparatively smaller Pollutant emissions.
  • switchover point relevant indicates at which Performance of the gas turbine from diffusion operation to premix operation is to be converted.
  • the gas and steam turbine plant with preheated intake air for the gas turbine has one comparatively lower switchover point so that they even with comparatively low load conditions for low Pollutant emissions more affordable premix operation is.
  • Steam turbine system 1 or 1 comprises a gas turbine system 1a and a steam turbine plant 1b.
  • the gas turbine plant 1a comprises a gas turbine 2 with a coupled air compressor 4.
  • the air compressor 4 is on the input side Intake air line 5 connected.
  • the gas turbine 2 is one Combustion chamber 6 connected upstream, to a fresh air line 8 of the air compressor 4 is connected.
  • the gas turbine 2 opens a fuel line 10.
  • the gas turbine 2 and the air compressor 4 and a generator 12 sit on a common shaft 14.
  • the steam turbine system 1b also includes a steam turbine 20 coupled generator 22 and in a water-steam cycle 24 a main condenser connected downstream of the steam turbine 20 26 and a heat recovery steam generator 30.
  • the steam turbine 20 consists of a first pressure stage or a High pressure part 20a and a second pressure stage or one Medium pressure part 20b and a third pressure stage or one Low pressure part 20c, the generator via a common shaft 32 22 drive.
  • AM 'or flue gas in the heat recovery steam generator 30 is one Exhaust line 34 to an input 30a of the heat recovery steam generator 30 connected.
  • the relaxed work equipment from AM ' the gas turbine 2 leaves the heat recovery steam generator 30 whose output 30b in the direction of a not shown Stack.
  • the heat recovery steam generator 30 comprises in a first pressure stage or high-pressure stage of the water-steam circuit 24 one High-pressure preheater or economizer 36, which has one with one Valve 38 lockable line 40 to a high pressure drum 42 is connected.
  • the high pressure drum 42 is with a arranged in the heat recovery steam generator 30 high pressure evaporator 44 to form a water-steam cycle 46.
  • To the Removing live steam F is the high pressure drum 42 to one High-pressure superheaters arranged in the heat recovery steam generator 30 48 connected, the outlet side with the steam inlet 49 of the high pressure part 20a of the steam turbine 20 is connected.
  • the steam outlet 50 of the high pressure part 20 a of the steam turbine 20 is via a steam line 52 ("cold ZÜ") with a reheater 54 connected, the output 56 via a Steam line 58 to the steam inlet 60 of the medium pressure part 20b of the steam turbine 20 is connected. Its steam outlet 62 is connected to the steam inlet 66 via an overflow line 64 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 via a feed water line 72, in a feed water pump 74 and a condensate preheater 76 are connected to the economizer 36, so that a closed water-steam circuit 24 is formed.
  • each of a medium or low pressure level of the water-steam circuit 24 are assigned. This Heating surfaces are appropriately connected to steam inlet 60 of the medium pressure part 20b of the steam turbine 20 or with the Steam inlet 66 of the low pressure part 20c of the steam turbine 20 connected.
  • the gas and steam turbine system 1, 1 ' is to achieve a designed for particularly high efficiency.
  • the condenser 80 is the steam turbine 20 via a valve 82 lockable bleed steam line 84 connected downstream.
  • On the output side is the capacitor 80 through a capacitor line 86 connected to the feed water line 72 so that a Water-steam side parallel connection of the capacitor 80 to the main capacitor 26 associated with the steam turbine 20.
  • the condensate line 86 is connected to the feed water line 72 connected to a feed point 88.
  • the feed point 88 is in the direction of flow from the main condenser 26 flowing condenser K seen behind the Condensate preheater 76 arranged. This is via valve 82 Vapor ratio between the main condenser 26 supplied partial steam flow and that supplied to the condenser 80 Partial steam flow adjustable. Through a variation This steam quantity ratio can be used for the current Power output of the gas and steam turbine system 1, 1 'the Intake air A preheated to the maximum attainable temperature become.
  • the gas and steam turbine plant 1 according to FIG. 1 is for one single-stage heat exchange between that in the condenser 80 to condensing partial steam flow and that of the gas turbine system 1a intake air to be supplied.
  • a capacitor 80 an air condenser is provided with cooling air can be acted upon as a cooling medium.
  • the capacitor 80 is in in this case, directly into the intake air line on the coolant side 5 switched.
  • the gas and steam turbine plant 1 are the in the heat transfer from the condensing in the condenser 80 Steam on the intake air A due to conversion processes resulting losses are kept particularly low.
  • Operation of the gas and steam turbine plant 1, 1 'with preheating of the intake air A by condensation bleed steam in the condenser 80 is thus suitable especially for the partial load range. Also in this mode a quick performance reserve in a particularly simple form the gas and steam turbine system 1, 1 ', because with a quick shutdown of the preheating the intake air A due to the then comparatively increased available total mass flow of working medium AM for the gas turbine 2 a rapid increase in power output Gas turbine 2 is enabled.

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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)
EP98958189A 1997-10-15 1998-10-05 Gas- und dampfturbinenanlage und verfahren zum betreiben einer derartigen anlage Expired - Lifetime EP1023526B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19745272 1997-10-15
DE19745272A DE19745272C2 (de) 1997-10-15 1997-10-15 Gas- und Dampfturbinenanlage und Verfahren zum Betreiben einer derartigen Anlage
PCT/DE1998/002941 WO1999019608A1 (de) 1997-10-15 1998-10-05 Gas- und dampfturbinenanlage und verfahren zum betreiben einer derartigen anlage

Publications (2)

Publication Number Publication Date
EP1023526A1 EP1023526A1 (de) 2000-08-02
EP1023526B1 true EP1023526B1 (de) 2003-02-12

Family

ID=7845457

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98958189A Expired - Lifetime EP1023526B1 (de) 1997-10-15 1998-10-05 Gas- und dampfturbinenanlage und verfahren zum betreiben einer derartigen anlage

Country Status (12)

Country Link
US (1) US6244035B1 (ko)
EP (1) EP1023526B1 (ko)
JP (1) JP4153662B2 (ko)
KR (1) KR100563517B1 (ko)
CN (1) CN1143949C (ko)
DE (2) DE19745272C2 (ko)
DK (1) DK1023526T3 (ko)
ES (1) ES2192799T3 (ko)
ID (1) ID24437A (ko)
RU (1) RU2200850C2 (ko)
UA (1) UA53748C2 (ko)
WO (1) WO1999019608A1 (ko)

Cited By (1)

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EP4080019B1 (en) * 2021-04-20 2024-01-10 General Electric Technology GmbH Gas turbine heat recovery system and method

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EP1736638A1 (de) * 2005-06-21 2006-12-27 Siemens Aktiengesellschaft Verfahren zum Hochfahren einer Gas- und Dampfturbinenanlage
KR100724801B1 (ko) * 2005-12-22 2007-06-04 한국항공우주연구원 가스터빈엔진의 흡기유동 시험장치
US8002714B2 (en) 2006-08-17 2011-08-23 Ethicon Endo-Surgery, Inc. Guidewire structure including a medical guidewire and method for using a medical instrument
US7934383B2 (en) * 2007-01-04 2011-05-03 Siemens Energy, Inc. Power generation system incorporating multiple Rankine cycles
RU2326247C1 (ru) * 2007-01-23 2008-06-10 Михаил Юрьевич Кудрявцев Способ работы парогазовой энергетической установки с замкнутым контуром циркуляции газа
EP2101051A1 (de) * 2008-03-12 2009-09-16 Siemens Aktiengesellschaft Speicherung elektrischer Energie mit Wärmespeicher und Rückverstromung mittels eines thermodynamischen Kreisprozesses
US7730712B2 (en) * 2008-07-31 2010-06-08 General Electric Company System and method for use in a combined cycle or rankine cycle power plant using an air-cooled steam condenser
FR2935737B1 (fr) 2008-09-10 2013-02-15 Suez Environnement Dispositif de cogeneration amelioree
EP2199547A1 (de) * 2008-12-19 2010-06-23 Siemens Aktiengesellschaft Abhitzedampferzeuger sowie ein Verfahren zum verbesserten Betrieb eines Abhitzedampferzeugers
ITVE20090055A1 (it) * 2009-10-02 2011-04-03 Giovanni Parise Aumento di efficienza degli impianti termoelettrici
EP2369145A1 (en) * 2010-03-09 2011-09-28 Siemens Aktiengesellschaft Power generation system and method
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US20120017597A1 (en) * 2010-07-23 2012-01-26 General Electric Company Hybrid power generation system and a method thereof
EP2503111B1 (en) * 2011-03-25 2016-03-02 Caterpillar Motoren GmbH & Co. KG Modular heat rejection system, direct organic rankine cycle system, and biomass combined cycle power generating system
DE102011006390A1 (de) * 2011-03-30 2012-10-04 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Durchlaufdampferzeugers und zur Durchführung des Verfahrens ausgelegter Dampferzeuger
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Also Published As

Publication number Publication date
WO1999019608A1 (de) 1999-04-22
DE19745272A1 (de) 1999-04-29
US6244035B1 (en) 2001-06-12
UA53748C2 (uk) 2003-02-17
ES2192799T3 (es) 2003-10-16
DE59807207D1 (de) 2003-03-20
KR100563517B1 (ko) 2006-03-27
CN1270656A (zh) 2000-10-18
KR20010024500A (ko) 2001-03-26
JP2001520342A (ja) 2001-10-30
EP1023526A1 (de) 2000-08-02
CN1143949C (zh) 2004-03-31
RU2200850C2 (ru) 2003-03-20
JP4153662B2 (ja) 2008-09-24
ID24437A (id) 2000-07-20
DE19745272C2 (de) 1999-08-12
DK1023526T3 (da) 2003-06-02

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