EP0840837B1 - Procede d'exploitation d'une installation de turbines a gaz et a vapeur et installation exploitee selon ce procede - Google Patents

Procede d'exploitation d'une installation de turbines a gaz et a vapeur et installation exploitee selon ce procede Download PDF

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Publication number
EP0840837B1
EP0840837B1 EP96922762A EP96922762A EP0840837B1 EP 0840837 B1 EP0840837 B1 EP 0840837B1 EP 96922762 A EP96922762 A EP 96922762A EP 96922762 A EP96922762 A EP 96922762A EP 0840837 B1 EP0840837 B1 EP 0840837B1
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EP
European Patent Office
Prior art keywords
steam
pressure
turbine
preheater
heat
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
EP96922762A
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German (de)
English (en)
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EP0840837A1 (fr
Inventor
Hermann Brückner
Georg Köhler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
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Siemens AG
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP0840837A1 publication Critical patent/EP0840837A1/fr
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Publication of EP0840837B1 publication Critical patent/EP0840837B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler

Definitions

  • the invention relates to a gas and steam turbine plant with one of the gas turbines connected downstream of the exhaust gas Heat recovery steam generator, its high-pressure preheater in the water-steam cycle the one having a low pressure part Steam turbine is switched. It continues to focus on one Plant operated according to this procedure.
  • the water-steam cycle includes several, e.g. two or three, pressure levels, each pressure level a preheater, an evaporator and a super heater having.
  • the invention is therefore based on the object of a gas and Steam turbine plant and a suitable one for its operation To further develop methods such that by a further increase the use of the heat content in the exhaust gas of the gas turbine an increase in system efficiency is achieved.
  • this problem is solved by a heat exchanger arranged outside the heat recovery steam generator, its primary side input to the output and its primary-side outlet to the inlet of the high-pressure preheater are connected, and the secondary side to a overflow line leading into the high pressure part of the steam turbine is switched.
  • the heat exchanger is on the primary side a circulation pump and a control valve.
  • a controller block serves to approximate the temperature of the via the heat exchanger High pressure preheater recirculated feed water to the temperature of the feed water fed directly to the high-pressure preheater with the aim that the temperatures at the mixing point of the high-pressure preheater are at least approximately the same.
  • a first temperature sensor with the controller module Detection of the temperature of the secondary side from the heat exchanger outflowing feed water connected.
  • a second with Temperature sensor connected to the controller module is used for detection the temperature of the high pressure preheater Feed water.
  • a particularly effective adaptation of the heating surface of the high pressure preheater the temperature profile of the exhaust gas from the This turns the gas turbine inside the heat recovery steam generator achieved that the high-pressure preheater has two stages is. Therefore, in a further advantageous embodiment the high pressure preheater and a first high pressure preheater second high-pressure preheater downstream of feed water, the one in the waste heat steam generator on the exhaust side before the first High pressure preheater is arranged.
  • This principle can be built up from three pressure levels Water-steam cycle can be further developed in that to that existing in a three-pressure ZÜ process Reheater a connected to this on the feed water side Medium pressure superheater is provided in the heat recovery steam generator arranged on the exhaust gas side before the reheater is. Furthermore, in order to further develop this principle Heat recovery steam generator arranged low pressure superheater provided be the output side with the secondary side Input of the heat exchanger is connected.
  • the stated task is thereby solved that the steam turbine incoming low pressure steam by indirect heat exchange with a high pressure preheater withdrawn partial flow of preheated feed water overheated becomes.
  • the cooled partial flow becomes the feed water to be preheated preferably mixed again at the inlet of the high pressure preheater, wherein a temperature approximation of the partial flow to the feed water to be preheated by adjusting the partial flow he follows.
  • the advantages achieved with the invention are in particular in that on the one hand by overheating the low pressure steam through indirect heat exchange outside the heat recovery steam generator with feed water preheated in the high-pressure preheater Heat from the exhaust gas from the gas turbine for overheating can be used, and that on the other hand due to the an additional degree of freedom compared to indirect heat exchange a direct heat exchange with the exhaust gas is provided becomes.
  • This additional degree of freedom enables heat transfer particularly favorable to the operating conditions present state of the low pressure steam from the steam turbine be adjusted. This makes it a particularly affordable one Exploitation of the heat content in the exhaust gas from the gas turbine too possible with changing load conditions.
  • the invention also enables an increase the generator clamping power of the steam turbine.
  • FIG. 1 An embodiment of the invention is based on a Drawing explained in more detail.
  • the figure shows schematically a gas and steam turbine system with a separate heat exchanger for heating low pressure steam.
  • the gas and steam turbine plant comprises one Gas turbine 2 and a steam turbine 4 and one from the hot Exhaust gas AG from the gas turbine 2 flows through the heat recovery steam generator 6.
  • the steam turbine 4 comprises a high pressure part 4a and a medium pressure part 4b and a low pressure part 4c.
  • the waste heat steam generator 6 is used to generate steam, wherein whose heating surfaces in a water-steam cycle 8 Steam turbine 4 are switched.
  • the heat recovery steam generator 6 has a condensate line 10 connected condensate preheater 12 on the on the input side via a condensate pump 14 with one of the Steam turbine 4 downstream capacitor 16 is connected.
  • the condensate preheater 12 is on the outlet side via a circulation pump 18 connected to its entrance. He is outgoing also via a feed line 20 with a feed water tank 22 connected.
  • the feed water tank 22 is on the output side via a Feed water line 24, into which a pump 26 is connected, connected to a low pressure drum 28.
  • a Feed water line 24 To the low pressure drum 28 is an evaporator via a circulation pump 30 connected.
  • the low-pressure drum 28 is also on the steam side a low pressure superheater 34 connected via a Steam line 36 to an overflow line 38 from the medium pressure part 4b connected to the low pressure part 4c of the steam turbine 4 is.
  • the low pressure drum 28 and the low pressure evaporator 32 together with the low pressure superheater 34 and the low pressure part 4c a low pressure stage of the water-steam cycle 8.
  • the feed water tank 22 is also on the output side a feed water line 40 into which a pump 42 is connected is connected to a first high-pressure preheater 44 which via a connecting line 46 to the input of a second High pressure preheater 48 is connected.
  • a medium pressure drum 52 via a line 50 connected, to which in turn via a circulation pump 54 Medium pressure evaporator 56 is connected.
  • the medium pressure drum 52 is on the steam side with a medium pressure superheater 56 connected, the output side with the input of a reheater 58 is connected.
  • the reheater 58 is on the input side of the high pressure part 4a and on the output side connected to the medium pressure part 4b of the steam turbine 4.
  • the medium pressure drum 52 and the medium pressure evaporator 56 as well as the medium pressure superheater 57 together with the Intermediate superheater 58 and the medium pressure part 4b of the steam turbine 4 a medium pressure stage of the water-steam cycle 8th.
  • the second high-pressure preheater 48 is on the output side via a Connection line 60 and a valve 62 with a high pressure drum 64 connected to the via a circulation pump 66 High pressure evaporator 68 is connected.
  • the high pressure drum 64 is on the steam side via a high-pressure superheater 70 the high pressure part 4a of the steam turbine 4 connected.
  • the High pressure preheaters 44, 48 and the high pressure drum 64 as well the high pressure evaporator 68 and the high pressure superheater 70 together with the high pressure part 4a of the steam turbine 4 a high-pressure stage of the water-steam cycle 8.
  • a heat exchanger 72 switched. Is primary the heat exchanger 72 on the input side via a line 74 the line 60 connected and thus with the output of the second high pressure preheater 48 connected.
  • the primary side Output of the heat exchanger 72 is via a line 76, in a pump 78 and a control valve 80 are connected with connected to the input of the second high pressure preheater 48.
  • the line 76 opens at a mixing point 82 in the the two high pressure preheaters 44 and 48 connecting line 46.
  • the condensate preheater becomes 12 via the pump 14 and the condensate line 10 capacitor K supplied from the capacitor 16. It can all or part of the condensate preheater 12 can be bypassed.
  • the condensate K is warmed up in the condensate preheater 12 and at least partially via the circulation pump 18 circulated.
  • the warmed condensate K is on the line 20 led into the feed water tank 22, where in a manner not shown a warming up of the Feed water takes place by means of bleed steam from the steam turbine 4.
  • the heated feed water S is the one hand Low pressure drum 28 and on the other hand via the first high pressure preheater 44 of the medium pressure drum 52 and the second high pressure preheater 48 fed to the high pressure drum 64.
  • the feed water S fed to the low pressure stage is evaporated at low pressure in the low-pressure evaporator 32, the one separated in the low pressure drum 28 Low pressure steam ND supplied to the low pressure superheater 34 becomes.
  • the overheated low pressure steam ND is there before Heat exchanger 72 led into the overflow line 38.
  • the feed water fed into the medium pressure drum 52 S evaporated in the medium pressure evaporator 56.
  • the Indian Medium pressure drum 52 separated, under medium pressure Standing steam is passed over the medium pressure superheater 57 and as superheated medium pressure steam MD the medium pressure part 4b of the steam turbine 4 supplied.
  • second high pressure preheater or economizer 48 preheated Feed water S in the high pressure evaporator 68 under high pressure evaporates, the one separated in the high pressure drum 64
  • High pressure steam HD in the high pressure superheater 70 overheated and in overheated state in the high pressure part 4a of the steam turbine 4 is performed.
  • the steam released in the high pressure part 4a becomes overheated again in reheater 58 and in superheated Condition together with that overheated in the medium pressure superheater 56
  • Medium pressure steam MD the medium pressure part 4b of the steam turbine 4 fed.
  • the steam in the medium-pressure part 4b of the steam turbine 4, which is under low pressure, is passed through the overflow line 38 and overheated in the heat exchanger 72 by indirect heat exchange with a partial flow t S of the feed water S preheated in the high-pressure preheater 48.
  • the steam flowing out of the medium-pressure part 4b is mixed with the low-pressure steam ND overheated in the low-pressure superheater 34 before the heat exchanger 72.
  • the low-pressure steam ND overheated in the heat exchanger 72 is expanded in the low-pressure part 4c of the steam turbine 4 and fed to the condenser 16 for condensation.
  • the amount of the partial flow t S of the feed water S preheated in the second high-pressure preheater 48 supplied to the heat exchanger 72 per unit of time is set by means of the control valve 80.
  • the setting is such that the temperature T 1 of the partial flow t S and the temperature T 2 of the feed water S to be preheated at the mixing point 82 are approximated to one another, preferably the same.
  • a controller module 84 is connected to the control valve 80 via a control line 85.
  • the controller module 84 is also connected via a control line 86 to a first temperature sensor 87 for detecting the temperature T 1 and via a control line 88 to a second temperature sensor. 89 connected to the detection of the temperature T 2 .
  • the clamping power which can be drawn from a (not shown) steam turbine generator increases by 1.3% to 2%. If the entire low-pressure steam quantity is correspondingly overheated in a two-pressure process, the increase in steam turbine output which is achieved in this way is more than 2.6%.

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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)
  • Commercial Cooking Devices (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)

Claims (10)

  1. Installation à turbine à gaz et à turbine à vapeur comportant un générateur (6) de vapeur à récupération de chaleur perdue qui est monté en aval de la turbine (2) à gaz côté gaz d'échappement et dont le préchauffeur (48) à haute pression est branché dans le circuit (8) eau-vapeur de la turbine (4) à vapeur comportant une partie (4c) de basse pression, caractérisée par un échangeur de chaleur (72) qui est monté à l'extérieur du générateur (6) de vapeur à récupération de chaleur perdue, dont l'entrée côté primaire et la sortie côté primaire sont raccordées respectivement à la sortie et à l'entrée du préchauffeur (48) à haute pression et qui est branché côté secondaire dans un conduit (38) de trop-plein débouchant dans la partie (4c) de basse pression de la turbine (4) à vapeur.
  2. Installation suivant la revendication 1, caractérisée en ce qu'une pompe (78) de circulation et une valve (80) de régulation sont montées côté primaire en aval de l'échangeur de chaleur (72).
  3. Installation suivant la revendication 1 ou 2, caractérisée par un module (84) régulateur pour régler la quantité d'eau (tS) d'alimentation envoyée par unité de temps à l'échangeur de chaleur (72) côté primaire.
  4. Installation suivant la revendication 3, caractérisée par un premier capteur (87) de température relié au module (84) régulateur pour détecter la température (T1) de l'eau (tS) d'alimentation s'écoulant de l'échangeur de chaleur (72) côté secondaire et par un deuxième capteur (89) de température relié au module (84) régulateur pour détecter la température (T2) de l'eau (S) d'alimentation envoyée au préchauffeur (48) à haute pression.
  5. Installation suivant l'une des revendications 1 à 4, caractérisée en ce que le préchauffeur (48) à haute pression est un deuxième préchauffeur à haute pression qui est monté en aval côté eau d'alimentation d'un premier préchauffeur (44) à haute pression et qui est monté dans le générateur (6) de vapeur à récupération de chaleur perdue en amont du premier préchauffeur (44) à haute pression côté gaz d'échappement.
  6. Installation suivant l'une des revendications 1 à 5, caractérisée par un surchauffeur (34) à basse pression qui est monté dans le générateur (6) de vapeur à récupération de chaleur perdue et qui communique côté sortie avec l'entrée côté secondaire de l'échangeur de chaleur (72).
  7. Procédé pour faire fonctionner une installation à turbine à gaz et à turbine à vapeur, dans lequel de la vapeur contenue dans le fluide (AG) de travail détendu sortant de la turbine (2) à gaz est utilisée pour produire de la vapeur pour la turbine (4) à vapeur montée dans un circuit (8) eau-vapeur constitué d'au moins deux étages de pression, de l'eau (S) d'alimentation s'écoulant dans le circuit (8) eau-vapeur étant préchauffée dans un préchauffeur (48) à haute pression monté dans le générateur (6) de vapeur à récupération de chaleur perdue, caractérisé en ce que la vapeur (ND) à basse pression affluant à la turbine (4) à vapeur est surchauffée par échange thermique indirect avec un courant (tS) partiel d'eau (S) d'alimentation préchauffée prélevée dans le préchauffeur (48) à haute pression.
  8. Procédé suivant la revendication 7, caractérisé en ce que le courant (tS) partiel refroidi est mélangé à l'eau (S) d'alimentation à préchauffer, la température (T1) du courant (tS) partiel et la température (T2) de l'eau (S) d'alimentation à préchauffer étant rapprochées l'une de l'autre.
  9. Procédé suivant la revendication 8, caractérisé en ce que l'on rapproche les températures en réglant le courant (tS) partiel.
  10. Procédé suivant l'une des revendications 7 à 9, comportant un circuit (8) eau-vapeur constitué de trois étages de pression, caractérisé en ce que de la vapeur (ND) à basse pression surchauffée dans le générateur (6) de vapeur à récupération de chaleur perdue est mélangée à la vapeur (ND) à basse pression à surchauffer par échange thermique indirect.
EP96922762A 1995-07-27 1996-07-10 Procede d'exploitation d'une installation de turbines a gaz et a vapeur et installation exploitee selon ce procede Expired - Lifetime EP0840837B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19527537A DE19527537C1 (de) 1995-07-27 1995-07-27 Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage sowie danach arbeitende Anlage
DE19527537 1995-07-27
PCT/DE1996/001244 WO1997005366A1 (fr) 1995-07-27 1996-07-10 Procede d'exploitation d'une installation de turbines a gaz et a vapeur et installation exploitee selon ce procede

Publications (2)

Publication Number Publication Date
EP0840837A1 EP0840837A1 (fr) 1998-05-13
EP0840837B1 true EP0840837B1 (fr) 2001-08-29

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Application Number Title Priority Date Filing Date
EP96922762A Expired - Lifetime EP0840837B1 (fr) 1995-07-27 1996-07-10 Procede d'exploitation d'une installation de turbines a gaz et a vapeur et installation exploitee selon ce procede

Country Status (11)

Country Link
US (1) US5992138A (fr)
EP (1) EP0840837B1 (fr)
JP (1) JPH11509901A (fr)
KR (1) KR19990029030A (fr)
CN (1) CN1093215C (fr)
DE (2) DE19527537C1 (fr)
ES (1) ES2163641T3 (fr)
RU (1) RU2153080C2 (fr)
TW (1) TW308627B (fr)
UA (1) UA41457C2 (fr)
WO (1) WO1997005366A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997007323A1 (fr) * 1995-08-18 1997-02-27 Siemens Aktiengesellschaft Installation a turbine a gaz et a vapeur et procede de fonctionnement de ladite installation ainsi que generateur de vapeur de chaleur perdue pour une telle installation
AT410695B (de) * 1996-03-08 2003-06-25 Beckmann Georg Dr Vorrichtung und verfahren zur energieerzeugung
JP4126108B2 (ja) * 1998-02-25 2008-07-30 三菱重工業株式会社 ガスタービンコンバインドプラント、その運転方法、及びガスタービン高温部蒸気冷却システム
DE19829088C2 (de) * 1998-06-30 2002-12-05 Man Turbomasch Ag Ghh Borsig Stromerzeugung in einem Verbundkraftwerk mit einer Gas- und einer Dampfturbine
US6796240B2 (en) * 2001-06-04 2004-09-28 Quad/Tech, Inc. Printing press register control using colorpatch targets
CN1948720B (zh) * 2006-10-31 2011-08-10 章祖文 永磁传动低温多级涡轮发电机
DE102008057490B4 (de) * 2008-11-14 2010-09-30 Siemens Aktiengesellschaft Kombiniertes Gas- und Dampfturbinenkraftwerk und Verfahren zum Betrieb
US9435534B2 (en) * 2009-08-31 2016-09-06 Holistic Engineering Inc Energy-recovery system for a production plant
RU2553477C2 (ru) * 2013-01-23 2015-06-20 Аркадий Ефимович Зарянкин Парогазовая установка
US11008897B2 (en) * 2016-06-17 2021-05-18 Siemens Energy Global GmbH & Co. KG Condensate recirculation
FI20210068A1 (fi) * 2021-11-10 2023-05-11 Loeytty Ari Veli Olavi Menetelmä ja laitteisto energiatehokkuuden parantamiseksi nykyisissä kaasuturbiini kombilaitoksissa

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH432555A (de) * 1965-02-15 1967-03-31 Sulzer Ag Dampfkraftanlage mit Dampferzeuger und mit Gasturbine
DE3804605A1 (de) * 1988-02-12 1989-08-24 Siemens Ag Verfahren und anlage zur abhitzedampferzeugung
DE59000787D1 (de) * 1989-07-27 1993-03-04 Siemens Ag Abhitzedampferzeuger fuer ein gas- und dampfturbinenkraftwerk.
DE4029991A1 (de) * 1990-09-21 1992-03-26 Siemens Ag Kombinierte gas- und dampfturbinenanlage
JPH04298604A (ja) * 1990-11-20 1992-10-22 General Electric Co <Ge> 複合サイクル動力装置及び蒸気供給方法
DE59205640D1 (de) * 1991-05-27 1996-04-18 Siemens Ag Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage und entsprechende Anlage
DE59205446D1 (de) * 1991-07-17 1996-04-04 Siemens Ag Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage und Anlage zur Durchführung des Verfahrens
DE59203883D1 (de) * 1991-07-17 1995-11-09 Siemens Ag Verfahren zum Betreiben einer Gas- und Dampfturbinenanlage und Anlage zur Durchführung des Verfahrens.

Also Published As

Publication number Publication date
EP0840837A1 (fr) 1998-05-13
CN1177995A (zh) 1998-04-01
DE59607594D1 (de) 2001-10-04
RU2153080C2 (ru) 2000-07-20
CN1093215C (zh) 2002-10-23
UA41457C2 (uk) 2001-09-17
ES2163641T3 (es) 2002-02-01
KR19990029030A (ko) 1999-04-15
US5992138A (en) 1999-11-30
DE19527537C1 (de) 1996-09-26
WO1997005366A1 (fr) 1997-02-13
JPH11509901A (ja) 1999-08-31
TW308627B (fr) 1997-06-21

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