EP0561220B1 - Procédé pour le fonctionnement d'une installation de génération de vapeur et générateur de vapeur - Google Patents

Procédé pour le fonctionnement d'une installation de génération de vapeur et générateur de vapeur Download PDF

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Publication number
EP0561220B1
EP0561220B1 EP93103393A EP93103393A EP0561220B1 EP 0561220 B1 EP0561220 B1 EP 0561220B1 EP 93103393 A EP93103393 A EP 93103393A EP 93103393 A EP93103393 A EP 93103393A EP 0561220 B1 EP0561220 B1 EP 0561220B1
Authority
EP
European Patent Office
Prior art keywords
steam
water
pressure
evaporator
preheated
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
EP93103393A
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German (de)
English (en)
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EP0561220A1 (fr
Inventor
Georg Dipl.-Ing. Lösel (FH)
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
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 EP0561220A1 publication Critical patent/EP0561220A1/fr
Application granted granted Critical
Publication of EP0561220B1 publication Critical patent/EP0561220B1/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
    • 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
    • F01K23/108—Regulating means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
    • F22D1/003—Feed-water heater systems

Definitions

  • the invention relates to a method for operating a plant for generating steam, in particular in a fossil-fired power plant, e.g. in a gas and steam turbine plant in which steam is generated from water by indirect heat exchange with hot flue gas, condensed water first being preheated and then the preheated water being evaporated under high pressure. It is also aimed at a plant operated according to this method.
  • the amount of heat contained in a hot flue gas in the steam generator is used to generate steam.
  • the flue gas is e.g. the hot exhaust gas flowing out of a gas turbine and the steam generator is e.g. a waste heat boiler downstream of the gas turbine.
  • the heating surfaces arranged in the steam generator and designed in the form of tubes or tube bundles are usually connected to the water-steam circuit of a steam turbine.
  • the water-steam cycle often comprises several pressure stages, each of which is made up of a preheater and an evaporator and a superheater.
  • a condensate preheater is additionally provided in the steam generator for heating up the condensed water from the steam turbine.
  • the amount of heat introduced into the steam generator differs in different operating states, the heating surfaces in the steam generator being designed for full-load operation.
  • a reduction in the flue gas temperature means that the steam generator has been brought in Reduced heat quantity, even if the mass flow of the flue gas remains almost constant.
  • the resulting reduction in the amount of steam produced results in a reduction in the total amount of water available in the water-steam cycle. This can undesirably lead to premature evaporation of the preheated and high-pressure water.
  • Such vapor formation in a high-pressure preheater (economizer) or at its outlet has a particularly disadvantageous effect on the mass distribution at the inlet of the tubes which are usually arranged parallel to one another in the high-pressure evaporator of the steam generator.
  • An unstable flow in the tubes, especially in the tubes of the high-pressure evaporator reduces above all the effectiveness of the heating surfaces, with the result that the efficiency of the system decreases. Unstable flow conditions can also damage the heating surfaces.
  • the invention is therefore based on the object of designing a method for operating a system for generating steam and such a system in such a way that the highest possible efficiency and stable flow conditions in the area of the heating surfaces are achieved in all operating states, in particular also in the part-load range.
  • this object is achieved according to the invention in that, at least in the part-load range, the preheated water, which is already under high pressure, is cooled by heat exchange with at least a partial stream of the condensed water.
  • the temperature of the water before evaporation and the temperature of the steam are determined, the difference between these temperatures serving as a variable for setting the partial flow. This in turn affects the temperature of the preheated and high pressure water.
  • a partial stream of the preheated and high-pressure water is expediently mixed into the condensed water.
  • the stated object is achieved according to the invention by a heat exchanger which is connected downstream of the condensate preheater and is connected upstream of the condensate preheater on the secondary side.
  • a temperature sensor is provided in an advantageous embodiment of the system for generating steam on the inflow side and on the outflow side of a high-pressure evaporator.
  • the temperature sensors are expediently connected via a control element to a valve connected in a condensate line.
  • the heat exchanger is expediently in a partial flow line which is a bypass to the condensate line.
  • the actual high-pressure evaporator has a further evaporator, i.e. a so-called residual evaporator or preheater. Inside the residual evaporator is the place or point of complete evaporation from which the steam overheats.
  • a good distribution of the water / steam mixture is achieved at the inlet of the tubes of the residual evaporator.
  • the residual evaporator was previously arranged in the flow direction of the hot flue gas behind the first high-pressure evaporator and was therefore in a region of comparatively cool flue gas temperature.
  • the residual evaporator is arranged upstream of the actual high-pressure evaporator in the flow direction of the flue gas.
  • the high-pressure evaporator is connected upstream of the residual evaporator and downstream of the condensate preheater within the water-steam cycle.
  • This circuit ensures that the specified distance between the temperature of the flue gas in the steam generator in the region of the outlet of the high-pressure evaporator and the temperature of the saturated steam in the high-pressure evaporator is reliably maintained.
  • This temperature gap also known as "pinch point" determines to a large extent the size of the heating surface of the high pressure evaporator. With this heating surface arrangement, a particularly small heating surface of the high-pressure evaporator and of the residual evaporator can be achieved, especially in stable flow conditions.
  • the illustrated system for steam generation comprises a steam generator 1, through which hot flue gas RG flows on the primary side.
  • the steam generator 1 is e.g. Part of a gas and steam turbine plant.
  • the cooled flue gas RG leaves the steam generator 1 - as indicated by the arrow 2 - in the direction of a chimney, not shown.
  • the flue gas RG is e.g. fossil-fired steam generator self-generated; but it can also be the hot exhaust gas from a gas turbine upstream of the steam generator 1.
  • the steam generator 1 is also referred to as a waste heat boiler or waste heat steam generator.
  • the steam generator 1 comprises a condensate preheater 3, a low-pressure heating device 10, a high-pressure heating device 20 and an intermediate superheater 25.
  • the low-pressure heating device 10 comprises a preheater 12 and an evaporator 14, which together with a water-steam drum 16 and a low-pressure part of a steam turbine, not shown, belong to the low-pressure stage of a water-steam circuit 18.
  • the high-pressure heating device 20 comprises two evaporators 22, 24 connected in series and a high-pressure superheater 26, which together with a high-pressure preheater or economizer 28 and a water-steam container 30 and a high-pressure part of the steam turbine, not shown, the high-pressure stage of the water - Form steam circuit 18.
  • the reheater 25 is connected in a manner not shown to a medium pressure part of the steam turbine.
  • condensed water K flows from a condenser (not shown) connected downstream of the steam turbine (not shown) via a condensate line 4 and through the condensate preheater 3 into a feed water tank 6.
  • a three-way valve 7 is connected to the condensate line 4.
  • part of the condensed water K preheated in the condensate preheater 3 is again conveyed through the condensate preheater 3 via a circulation pump 8.
  • water flows via a feed water pump 9 into the low-pressure preheater 12 and from there into the water-steam drum 16.
  • water and steam are separated from one another.
  • the water is fed through a pump 11 through the low-pressure evaporator 14 and from there it is returned to the separating drum 16 as steam.
  • the steam is fed to the low-pressure part of the steam turbine via a line 13.
  • Pre-warmed water W is also taken from the feed water tank 6 via a high-pressure pump 21 and is conveyed under high pressure via a line 23 into the economizer 28. From there, the preheated and high-pressure water W flows into the evaporators 22 and 24.
  • the economizer 28 and the evaporators 22 and 24 are first fed through with a predetermined water flow, the water being collected in the water-steam separating container 30 and being discharged from there via a line 29 into an expansion tank 31.
  • a valve 32 is connected in line 29. The water is discharged from the expansion tank 31 under atmospheric pressure via a line 33.
  • the economizer 28 and the evaporators 22 and 24 flowing in preheated and under high pressure water W are cooled by heat exchange with the condensed water K, at least a partial stream t 1 of the condensed water K.
  • a heat exchanger 40 is provided, which is located on the one hand in line 23 and on the other hand in a partial flow line 41 of the condensate line 4.
  • the partial flow line 41 is connected to the condensate line 4 both on the input side via the three-way valve 7 and on the output side.
  • the heat exchanger 40 is thus connected on the primary side to the condensate preheater 3 and on the secondary side to the condensate preheater 3.
  • the partial stream t1 of the condensed water K is regulated.
  • the three-way valve 7 is connected to a control device 43.
  • the control device 43 is connected via connections 44 and 45 to temperature sensors 46 and 47, respectively.
  • the temperature sensor 46 With the temperature sensor 46, the temperature T 1 of the water entering the evaporator 22 is determined.
  • the temperature sensor 47 With the temperature sensor 47, the temperature T2 of the steam or water-steam mixture flowing out of the evaporator 22 is determined.
  • the difference between these two temperatures T 1 and T 2 determined in the control device 43 serves as a controlled variable for setting the three-way valve 7 and thus the partial flow t 1.
  • the temperature T3 of the preheated and high-pressure water W is set such that when the water enters the evaporator 22 it is only slightly but surely below the boiling temperature.
  • an adjustable partial stream t2 of the preheated and high-pressure water W is mixed with it.
  • a line 50 is connected on the output side to the high-pressure pump 21 and is connected to the condensate line 4.
  • a valve 51 is connected in line 50.
  • the heating surfaces of the steam generator 1 are usually each formed from tube bundles with a large number of individual tubes.
  • the tubes of the individual heating surfaces open both on the input side and on the output side into collecting containers, which are represented by circles in the drawing at the inputs and outputs of the heating surfaces.
  • the collecting containers are connected to one another in accordance with the respectively predetermined circuit via connecting pipes and connected into the water-steam circuit 18. This makes it possible to assemble different modules with different heating surfaces as required.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)

Claims (8)

  1. Procédé pour faire fonctionner une installation de production de vapeur, notamment une centrale nucléaire à combustible fossile, par exemple dans une installation à turbines à gaz et à vapeur, dans laquelle de la vapeur est produite à partir de l'eau, par échange de chaleur indirect avec un gaz de fumée chaud (RG), de l'eau condensée (K) étant tout d'abord préchauffée, puis l'eau préchauffée (W) vaporisée sous pression,
    caractérisé par le fait qu'au moins dans la gamme de charges partielles, l'eau préchauffée est déjà placée sous haute pression (W) et est refroidie par échange thermique avec au moins un courant partiel (t₁) de l'eau condensée (K).
  2. Procédé suivant la revendication 1, caractérisé par le fait que la température (T₁) de l'eau avant l'évaporation et la température (T₂) de la vapeur sont déterminées et que la différence de ces températures (T₁, T₂) est utilisée comme grandeur pour le réglage du courant partiel (t₁).
  3. Procédé suivant la revendication 1 ou 2, caractérisé par le fait qu'un courant partiel (t₂) de l'eau préchauffée et placée sous haute pression (W) est mélangé à l'eau condensée (K).
  4. Installation de production de vapeur comportant un générateur de vapeur (1) traversé par un gaz de fumée chaud (RG) et dont une surface de chauffe est un réchauffeur à condensat (3), caractérisée par un échangeur de chaleur (40) dont le côté primaire est monté en aval du réchauffeur formant condensat (3) ou dont le côté secondaire est monté en amont du réchauffeur à condensat (3).
  5. Installation suivant la revendication 4, dont l'autre surface de chauffe est un évaporateur à haute pression (22), caractérisée par le fait que sur le côté alimentation et sur le côté évacuation de l'évaporateur à haute pression (22) sont prévus des capteurs respectifs de température (46 et 47), qui sont reliés, par l'intermédiaire d'un dispositif de régulation (43), à une soupape (7) montée dans une canalisation à condensat (4).
  6. Installation suivant la revendication 5, caractérisée par le fait qu'un autre évaporateur (24) est monté en aval de l'évaporateur à haute pression (22), l'autre évaporateur (24) étant disposé, dans le générateur de vapeur (1), en amont de l'évaporateur à haute pression (22) dans la direction de circulation du gaz de fumée (RG).
  7. Installation suivant l'une des revendications 4 à 6, caractérisée par le fait que l'échangeur de chaleur (40) est situé, côté secondaire, dans une canalisation de courant partiel (41), qui est une voie de contournement de la canalisation à condensat (4).
  8. Installation à turbines à gaz et à vapeur comportant une installation de production de vapeur suivant l'une des revendications 4 à 7.
EP93103393A 1992-03-16 1993-03-03 Procédé pour le fonctionnement d'une installation de génération de vapeur et générateur de vapeur Expired - Lifetime EP0561220B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4208397 1992-03-16
DE4208397 1992-03-16

Publications (2)

Publication Number Publication Date
EP0561220A1 EP0561220A1 (fr) 1993-09-22
EP0561220B1 true EP0561220B1 (fr) 1995-09-13

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ID=6454201

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EP93103393A Expired - Lifetime EP0561220B1 (fr) 1992-03-16 1993-03-03 Procédé pour le fonctionnement d'une installation de génération de vapeur et générateur de vapeur

Country Status (4)

Country Link
US (1) US5293842A (fr)
EP (1) EP0561220B1 (fr)
JP (1) JPH0626606A (fr)
DE (1) DE59300573D1 (fr)

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DE19736885A1 (de) * 1997-08-25 1999-03-04 Siemens Ag Dampferzeuger, insbesondere Abhitzedampferzeuger und Verfahren zum Betrieb dieses Dampferzeugers
EP0919767B1 (fr) * 1997-12-01 2002-06-05 Alstom Centrale combinée gaz-vapeur avec un générateur de vapeur à passage unique
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EP1710498A1 (fr) * 2005-04-05 2006-10-11 Siemens Aktiengesellschaft Générateur de vapeur
JP4842007B2 (ja) * 2006-05-02 2011-12-21 バブコック日立株式会社 排熱回収ボイラ
JP4842071B2 (ja) * 2006-09-26 2011-12-21 バブコック日立株式会社 貫流式排熱回収ボイラの運転方法、ならびに発電設備の運転方法
WO2009106563A2 (fr) * 2008-02-26 2009-09-03 Alstom Technology Ltd Procédé de régulation d'un générateur de vapeur et circuit de régulation pour générateur de vapeur
EP2182278A1 (fr) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Générateur de vapeur en continu
EP2199547A1 (fr) * 2008-12-19 2010-06-23 Siemens Aktiengesellschaft Générateur de vapeur pour récupérer la chaleur et procédé de fonctionnement amélioré d'un générateur de vapeur pour récupérer la chaleur
NL2003596C2 (en) * 2009-10-06 2011-04-07 Nem Bv Cascading once through evaporator.
DE102010028426A1 (de) 2010-04-30 2011-11-03 Siemens Aktiengesellschaft Dampferzeuger
DE102010028720A1 (de) * 2010-05-07 2011-11-10 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Dampferzeugers
EP2834561B1 (fr) 2012-01-17 2021-11-24 General Electric Technology GmbH Agencement de tubes dans un évaporateur horizontal à passage unique
KR101697816B1 (ko) 2012-01-17 2017-01-18 제네럴 일렉트릭 테크놀러지 게엠베하 관류형 수평 증발기의 섹션들을 연결하기 위한 방법 및 장치
US10100680B2 (en) 2013-09-19 2018-10-16 Siemens Aktiengesellschaft Combined cycle gas turbine plant comprising a waste heat steam generator and fuel preheating step
EP2940381B1 (fr) * 2014-04-28 2016-12-28 General Electric Technology GmbH Système de préchauffage de milieu fluide
CN106461206B (zh) * 2014-04-28 2020-04-10 通用电器技术有限公司 用于流体介质预热的系统和方法
EP3048366A1 (fr) * 2015-01-23 2016-07-27 Siemens Aktiengesellschaft Générateur de vapeur à récupération de chaleur
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DE102018002086A1 (de) * 2018-03-09 2019-09-12 Borsig Gmbh Quenchsystem
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Also Published As

Publication number Publication date
EP0561220A1 (fr) 1993-09-22
US5293842A (en) 1994-03-15
DE59300573D1 (de) 1995-10-19
JPH0626606A (ja) 1994-02-04

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