EP0840837A1 - 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

Info

Publication number
EP0840837A1
EP0840837A1 EP96922762A EP96922762A EP0840837A1 EP 0840837 A1 EP0840837 A1 EP 0840837A1 EP 96922762 A EP96922762 A EP 96922762A EP 96922762 A EP96922762 A EP 96922762A EP 0840837 A1 EP0840837 A1 EP 0840837A1
Authority
EP
European Patent Office
Prior art keywords
pressure
steam
steam turbine
low
feed water
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.)
Granted
Application number
EP96922762A
Other languages
German (de)
English (en)
Other versions
EP0840837B1 (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
Original Assignee
Siemens AG
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 AG filed Critical Siemens AG
Publication of EP0840837A1 publication Critical patent/EP0840837A1/fr
Application granted granted Critical
Publication of EP0840837B1 publication Critical patent/EP0840837B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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 system with a waste heat steam generator connected downstream of the gas turbine on the exhaust gas side, the high pressure preheater of which is connected to the water / steam circuit of the steam turbine having a low pressure part. It is also aimed at a plant operated according to this method.
  • the heat contained in the relaxed working fluid from the gas turbine is used to generate steam for the steam turbine.
  • the heat transfer takes place by means of a number of heating surfaces which are arranged in the form of tubes or tube bundles in a heat recovery steam generator downstream of the gas turbine. These in turn are connected to the steam turbine water-steam cycle.
  • the water-steam cycle comprises several, e.g. two or three pressure levels, each pressure level having a preheater, an evaporator and a superheater.
  • the arrangement of the heating surfaces within the heat recovery steam generator is adapted to the temperature profile of the exhaust gas.
  • the so-called three-pressure ZÜ process a particularly high steam turbine output and thus a particularly high overall efficiency of the plant are achieved with a given gas turbine output.
  • a gas and steam turbine plant operating according to the three-pressure ZÜ process is known from EP 0 436 536 B1. But even with this well-known system, the overall efficiency is limited to around 55%.
  • the invention is therefore based on the object of developing a gas and steam turbine system and a method suitable for its operation in such a way that an increase in the system efficiency is achieved by further increasing the use of the heat content in the exhaust gas of the gas turbine.
  • this object is achieved by a heat exchanger arranged outside the heat recovery steam generator, the primary-side inlet of which is connected to the outlet and the primary-side outlet of which is connected to the inlet of the high-pressure preheater, and the secondary-side is connected to an overflow conduit opening into the high-pressure part of the steam turbine device is switched.
  • a circulation pump and a control valve are connected on the primary side of the heat exchanger.
  • a controller module is expediently provided for setting the amount of feed water supplied per unit time on the primary side of the heat exchanger.
  • the controller module serves to approximate the temperature of the feed water returned via the heat exchanger to the high-pressure preheater 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 for detecting the temperature of the feed water flowing out of the heat exchanger on the secondary side is connected to the controller module.
  • a second temperature sensor connected to the controller module is used to measure the temperature of the high-pressure preheater
  • the high-pressure preheater is designed in two stages. Therefore, in a further advantageous embodiment the high-pressure preheater is a second high-pressure preheater downstream of a first high-pressure preheater, which is arranged in the waste heat steam generator in front of the first high-pressure preheater.
  • This principle can be developed further in a water-steam circuit constructed from three pressure stages in that, in addition to the intermediate superheater present in a three-pressure ZÜ process, a medium-pressure superheater is provided in the waste heat which is connected to the feed water side steam generator is arranged on the exhaust gas side before the reheater.
  • a low-pressure superheater arranged in the waste heat steam generator can be provided, which is connected on the outlet side to the secondary-side inlet of the heat exchanger.
  • the stated object is achieved in that the low-pressure steam flowing to the steam turbine is overheated by indirect heat exchange with a preheated feedwater taken from the high-pressure preheater.
  • the cooled sub-stream is preferably mixed again with the feed water to be preheated at the inlet of the high-pressure preheater, the sub-stream approaching the temperature of the feed water to be preheated by adjusting the sub-stream.
  • superheated low-pressure steam is further superheated in the waste heat steam generator by mixing it with the low-pressure steam to be overheated by indirect heat exchange.
  • the advantages achieved with the invention are in particular that, on the one hand, overheating of the low-pressure steam through indirect heat exchange outside the waste heat Steam generator with preheated in the high pressure preheater feed water heat from the exhaust gas of the gas turbine can be used for overheating, and that on the other hand an additional degree of freedom compared to a direct heat exchange with the exhaust gas is provided due to the indirect heat exchange.
  • the heat transfer can be adapted particularly favorably to the operating condition of the low-pressure steam from the steam turbine. This enables a particularly favorable utilization of the heat content in the exhaust gas from the gas turbine, even under changing load conditions.
  • the invention also enables the generator clamping power of the steam turbine to be increased.
  • FIG. 1 shows schematically a gas and steam turbine plant with a separate heat exchanger for heating low-pressure steam.
  • the gas and steam turbine system comprises a gas turbine 2 and a steam turbine 4 and a heat recovery steam generator 6 through which hot exhaust gas AG flows from the gas turbine 2.
  • 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, the heating surfaces of which are connected to a water-steam circuit 8 of the steam turbine 4.
  • the waste heat steam generator 6 has a condensate preheater 12 connected to a condensate line 10, which is connected on the input side via a condensate pump 14 to a condenser 16 connected downstream of the steam turbine 4.
  • the condensate preheater 12 is connected on the output side to its input via a circulation pump 18. It is also connected to a feed water container 22 via a feed line 20 via a feed line.
  • the feed water container 22 is connected on the output side to a low-pressure drum 28 via a feed water line 24, into which a pump 26 is connected.
  • An evaporator is connected to the low-pressure drum 28 via a circulation pump 30.
  • the low-pressure drum 28 is connected on the steam side to a low-pressure superheater 34, which is connected via a steam line 36 to an overflow line 38 from the medium-pressure part 4b to the low-pressure part 4c of the steam turbine 4.
  • the low-pressure drum 28 and the low-pressure evaporator 32 together with the low-pressure superheater 34 and the low-pressure part 4c form a low-pressure stage of the water-steam circuit 8.
  • the feed water tank 22 is also connected via a feed water line 40, into which a pump 42 is connected, to a first high-pressure preheater 44, which is connected via a connecting line 46 to the input of a second high-pressure preheater 48.
  • a medium-pressure drum 52 is connected to the connecting line 46 via a line 50, to which in turn a medium-pressure evaporator 56 is connected via a circulation pump 54.
  • the medium-pressure drum 52 is connected on the steam side to a medium-pressure superheater 56, which is connected on the output side to the input of an intermediate superheater 58.
  • the intermediate superheater 58 is connected on the input side to the high-pressure part 4a and on the output side to the medium-pressure part 4b of the steam turbine 4.
  • the medium-pressure drum 52 and the medium-pressure evaporator 56 and the medium-pressure superheater 57 together with the intermediate superheater 58 and the medium-pressure part 4b of the steam turbine 4 form a medium-pressure stage of the water-steam circuit
  • the second high-pressure preheater 48 is connected on the output side via a connecting line 60 and a valve 62 to a high-pressure drum 64, to which a high-pressure evaporator 68 is connected via a circulating pump 66.
  • the high pressure drum mel 64 is connected on the steam side via a high-pressure superheater 70 to the high-pressure part 4a of the steam turbine 4.
  • the secondary side of a heat exchanger 72 is connected in the overflow line 38 between the medium pressure part 4b and the low pressure part 4c of the steam turbine 4.
  • the heat exchanger 72 is connected on the input side to the line 60 via a line 74 and is thus connected to the output of the second high-pressure preheater 48.
  • the primary-side output of the heat exchanger 72 is connected to the input of the second high-pressure preheater 48 via a line 76, into which a pump 78 and a control valve 80 are connected.
  • the line 76 opens at a mixing point 82 into the line 46 connecting the two high-pressure preheaters 44 and 48.
  • the condensate preheater 12 When the gas and steam turbine system is operating, the condensate preheater 12 is supplied with condenser K from the condenser 16 via the pump 14 and the condensate line 10.
  • the condensate preheater 12 can be bypassed in whole or in part.
  • the condensate K is warmed up in the condensate preheater 12 and for this purpose at least partially circulated via the circulating pump 18.
  • the warmed-up condensate K is fed via line 20 into the feed water tank 22, "where the feed water is heated in a manner not shown by means of tapped steam from the steam turbine 4.
  • the warmed up feed water S becomes one side of the low-pressure drum 28 and on the other hand, to the medium-pressure drum 52 via the first high-pressure preheater 44 and to the high-pressure drum 64 via the second high-pressure preheater 48.
  • the feed water S fed to the low-pressure stage is ver ⁇ in the low-pressure evaporator 32 at low pressure vapors, the separated in the low pressure drum 28
  • Low pressure steam ND is fed to the low pressure superheater 34.
  • the low-pressure steam ND overheated there is conducted upstream of the heat exchanger 72 into the overflow line 38.
  • the feed water S fed into the medium-pressure drum 52 is evaporated in the medium-pressure evaporator 56.
  • the steam which is separated from the medium-pressure drum 52 and is under medium pressure is passed through the medium-pressure superheater 57 and is supplied as the superheated medium-pressure steam MD to the medium-pressure part 4b of the steam turbine 4.
  • the feed water S preheated in the second high-pressure preheater or economizer 48 is evaporated under high pressure in the high-pressure evaporator 68, the high-pressure steam HD separated in the high-pressure drum 64 overheating in the high-pressure superheater 70 and in the overheated state into the high-pressure part 4a the steam turbine
  • the steam released in the high-pressure part 4a is superheated again in the intermediate superheater 58 and, in the superheated state, is fed to the medium-pressure part 4b of the steam turbine 4 together with the medium-pressure steam MD superheated in the medium-pressure superheater 56.
  • the steam in the medium-pressure part 4b of the steam turbine 4, which is under low pressure, is passed over the overflow line 38 and in the heat exchanger 72 by indirect heat exchange with a partial flow tg of the feed water preheated in the high-pressure preheater 48 via the line 74
  • 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 tg of the feed water S which is supplied to the heat exchanger 72 per unit of time and is preheated in the second high-pressure preheater 48 is set by means of the control valve 80.
  • the setting is such that the The temperature T] of the partial flow tg and the temperature T2 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 to detect the temperature T 2.
  • the clamping power which can be obtained from a 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 ducting achieved is more than 2.6%.

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

Abstract

Cette installation de turbines à gaz et à vapeur comprend un générateur de vapeur (6) de chaleur perdue monté en aval du côté des gaz de combustion de l'installation et dont le récupérateur de chaleur perdue à haute pression (48) est raccordé au circuit d'eau et de vapeur (8) de la turbine à vapeur (4) pourvue d'une partie à basse pression (4c). Afin d'atteindre un rendement aussi élevé que possible, un échangeur de chaleur (72) monté à l'extérieur du générateur de vapeur de chaleur perdue (6) présente une admission côté primaire raccordée à la sortie du récupérateur de chaleur perdue à haute pression (48) et une sortie côté primaire raccordée à l'admission du récupérateur (48). L'échangeur de chaleur (72) est en outre raccordé du côté secondaire à une conduite de passage de la vapeur (38) qui débouche dans la partie à basse pression (4c) de la turbine à vapeur (4). Selon un procédé correspondant d'exploitation d'une installation de ce type, la vapeur sous basse pression (ND) qui afflue à la turbine à vapeur (4) est surchauffée par échange indirect de chaleur avec un courant partiel (tS) d'eau d'alimentation préchauffée, prélevé dans le récupérateur de chaleur perdue à haute pression (48).
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 true EP0840837A1 (fr) 1998-05-13
EP0840837B1 EP0840837B1 (fr) 2001-08-29

Family

ID=7767972

Family Applications (1)

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

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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.

Non-Patent Citations (1)

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Title
See references of WO9705366A1 *

Also Published As

Publication number Publication date
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
EP0840837B1 (fr) 2001-08-29
WO1997005366A1 (fr) 1997-02-13
JPH11509901A (ja) 1999-08-31
TW308627B (fr) 1997-06-21

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