EP0054601B1 - Chaudière à vapeur à circulation forcée - Google Patents

Chaudière à vapeur à circulation forcée Download PDF

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Publication number
EP0054601B1
EP0054601B1 EP81100601A EP81100601A EP0054601B1 EP 0054601 B1 EP0054601 B1 EP 0054601B1 EP 81100601 A EP81100601 A EP 81100601A EP 81100601 A EP81100601 A EP 81100601A EP 0054601 B1 EP0054601 B1 EP 0054601B1
Authority
EP
European Patent Office
Prior art keywords
evaporator
tubes
water
forming
final
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
Application number
EP81100601A
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German (de)
English (en)
Other versions
EP0054601B2 (fr
EP0054601A1 (fr
Inventor
Pawel Miszak
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.)
ABB Management AG
Original Assignee
Gebrueder Sulzer 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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=4352617&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0054601(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Gebrueder Sulzer AG filed Critical Gebrueder Sulzer AG
Publication of EP0054601A1 publication Critical patent/EP0054601A1/fr
Publication of EP0054601B1 publication Critical patent/EP0054601B1/fr
Application granted granted Critical
Publication of EP0054601B2 publication Critical patent/EP0054601B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F22B29/12—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes operating with superimposed recirculation during starting and low-load periods, e.g. composite boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F22B29/061—Construction of tube walls
    • F22B29/062—Construction of tube walls involving vertically-disposed water tubes

Definitions

  • the invention relates to a forced-flow steam generator system with the features of the preamble of claim 1.
  • Such a system is known from FR-PS 1 574 394.
  • the water separator is switched on between the wall-forming evaporator heating surface and the connected wall-forming, first superheater heating surface on the working medium side.
  • the water outlet of this separator is connected, on the one hand, to the inlet of the evaporator heating surface via a circulation pump and, on the other hand, is provided with a drain line in which a valve controlled by level in the separator is arranged.
  • the level-dependent control signal also acts on the feed pump.
  • Another separator is connected to the outlet of the wall-forming superheater heating surface, the water outlet of which is connected to the feed water line and the steam outlet of which is connected to a bulkhead superheater heating surface which is suspended in the combustion chamber near its outlet.
  • the further water separator which can be bridged on the steam side by means of a bypass line, has the purpose of taking up the excess water that is supplied to the evaporator when starting up and not separated by the first water separator and returning it to the feed water line. The water not separated by the first water separator therefore also flows through the wall-forming superheater heating surface before it reaches the further separator.
  • a further disadvantage of the steam generator which operates above the limit load of 50% of full load with forced passage and below this limit load with forced circulation, is that a switchover must take place when the limit load is passed, by switching on the level control signal of the first separator as the load increases and the circulation pump must be switched off, whereas with decreasing load the level control signal must be switched off while the circulation pump is switched on.
  • the second separator is taken out of operation when the load increases by opening the bypass line. Due to the fact that water flows through the wall-forming superheater heating surface at partial load, the efficiency is reduced, and more so the lower the load. Since the drain line is shut off during forced circulation operation of the known steam generator, this mode of operation cannot be maintained for a long time because salt deposits occur in the evaporator.
  • the known steam generator which is mainly intended for base load, is therefore not suitable for continuous operation at part load or for rapid load changes.
  • the invention has for its object to improve a forced-flow steam generator system of the type mentioned so that it enables safe continuous operation at part load and, moreover, rapid load changes and that the design effort is reduced.
  • the provision of the final evaporator between the wall-forming evaporator and the water separator prevents water from the wall-forming evaporator from reaching the wall-forming superheater heating surface at low partial load. This heating surface is thus protected from temperature shocks, and the efficiency of the steam generator system is also improved.
  • a mixing section is created in the connecting line from the wall-forming evaporator to the final evaporator, which ensures that the working fluid that emerges from the wall-forming evaporator, some of which is still undevaporated, has been heated differently when it flows through this evaporator is present as a homogeneous mixture at the inlet into the final evaporator.
  • the final evaporator thus compensates for the disadvantage of uneven heating, which is caused by the vertical arrangement of the tubes of the wall-forming evaporator.
  • Another advantage of attaching the final evaporator is that the wall-forming evaporator can be designed so that there is always a certain one at its outlet There is water in the flow of working fluid. This ensures good cooling of this evaporator.
  • the feature according to claim 3 allows the combustion chamber walls to be subjected to higher thermal loads. With these walls, the side of the tubes exposed to the flame radiation is heated to a greater extent, so that film evaporation can occur on the inside facing this heating, which leads to inadmissible tube wall temperatures.
  • the helically arranged grooves on the inside of the working medium are forced to rotate due to its longitudinal flow, as a result of which the heavier, liquid phase of the working medium is centrifuged against the wall. It is thus possible to increase the thermal strength of the pipes beyond what is to be expected from the increase in surface area.
  • a feed water line 15 with a feed pump 16 and two high-pressure preheaters 17 and 18 leads from the water area of the feed water container 13 to the input of an economizer 20 of a once-through steam generator 22.
  • the outlet of the economizer 20 is connected via a connecting line 23 to the distributor 25 of an evaporator heating surface 26.
  • This consists of tubes 27 tightly welded to one another, which form a funnel-shaped base 28 and four flat walls 29 of a combustion chamber 30 of the steam generator 22. In the walls 29, the tubes 27 run vertically; in section A they are provided with helical internal grooves.
  • the combustion chamber 30 has a furnace 32.
  • the wall-forming tubes 27 are alternately bent outwards from the walls 29 at the height of one and the other of two horizontal planes E and F and led to collectors 35. These collectors 35 are connected via a line 36 to a final evaporator 40, which consists of a system of finned tubes 41 and is arranged in a flue gas duct 60 starting from the combustion chamber 30 directly below the economizer 20.
  • the outlet of the final evaporator 40 is connected via a line 42 to the inlet of a water separator 44, from the bottom of which a line 45 with a level-controlled valve 46 leads back to the feed water vessel 13.
  • a connecting pipe 50 is connected, which opens into a ring distributor 51, from which wall pipes 53 lead to a ring collector 55.
  • the wall tubes 53 alternately enter the combustion chamber walls 29 in the horizontal planes E and F. They are tightly welded to one another and to the tubes 27, so that the flue gas duct 60 connects seamlessly to the combustion chamber 30.
  • the train 60 is bounded in its uppermost part by uncooled sheet metal walls 62 and a ceiling 63, to which a chimney 65 connects.
  • a second superheater 72 and a final superheater 75 are connected in series to the collector 55 of the wall pipes 53 forming a first superheater, and a live steam line 77 leads from the outlet of the final superheater 75 to a high-pressure turbine 78, the outlet of which is via a supply line 80 connected to an intermediate superheater 82 which is arranged in the flue gas flue 60 between the two superheaters 72 and 75.
  • a return line 84 leads to a low-pressure turbine 86 which, together with the high-pressure turbine 78 and a generator 88, sits on a common shaft and forms the turbine group 2.
  • the condensate treatment system 8 is designed such that the treated condensate has practically no salt, which has a conductivity of 0.2 u. Siemens corresponds, and that the silicon content is below 0.02 ppm. This means that salt deposits in the evaporator are negligible.
  • the additional water treatment plant 5 serves to relieve the condensate treatment plant ge 8 as well as the protection of the capacitor 1.
  • the system is particularly suitable for sliding pressure operation, with supercritical pressure prevailing in full load operation. In the following description of the operation of the system, it is initially assumed that the feed pump delivers subcritical pressure, since this condition also occurs at part load in systems operated under sliding pressure, which are operated at full load with supercritical pressure.
  • the condensate accumulating in the condenser 1 is practically completely desalinated together with the make-up water flowing in via line 3 in the condensate treatment system 8, which preferably contains a cation exchanger, a CO z -riesler, an anion exchanger and a mixed bed filter. It is then heated by the two preheaters 9 and 10, which are connected to the two lowermost withdrawals 11 of the low-pressure turbine 86 in a manner not shown, and fed into the degasser 12, from which it flows into the feed vessel 13.
  • the working fluid - now no longer called condensate, but feed water - is now brought to a pressure dependent on the load of the system, possibly supercritical pressure at full load, by the feed pump.
  • the feed water is heated in the two high-pressure preheaters 17 and 18, which are fed with bleed steam from two tapping points 19 of the low-pressure turbine 86.
  • a further heating in the assumed operation with subcritical pressure close to the evaporation temperature, takes place in the economizer 20.
  • the water is divided as evenly as possible onto the tubes 27.
  • adjustable throttling elements are installed in the mouths of the tubes 27. Since the heating of the individual pipes is not exactly the same among themselves, the working fluid flows of the individual pipes absorb an uneven amount of heat and accordingly an unevenly large amount of water evaporates in the different pipes.
  • the steam / water mixture of different water content flowing into the collector 35 is mixed on its way through the line 36 and - with possibly still considerable differences in the water content - distributed into the parallel pipes 41 of the final evaporator 40. Since the final evaporator 40 is arranged in a weakly heated area of the flue gas stream, that is to say in an area where the flue gas temperature is not much higher than the temperature of the evaporating water, its flue gas-side surface can, even if the working medium is distributed very unevenly on the pipes, do not assume dangerously high temperatures.
  • the working medium flows from the final evaporator 40, preferably slightly overheated at full load, into the separator 44. After any water that may still have been separated there, the now dry steam flows through the first superheater at a high speed, which guarantees good heat transfer, and a homogeneous temperature forming wall tubes 53.
  • the temperature difference between the welded tubes 27 of the evaporator 26 and the tubes 53 of the first superheater is mainly determined by the position of the final evaporator 40 in the flue gas stream. This position is chosen so that the temperature difference mentioned does not lead to inadmissibly high thermal stresses.
  • means for influencing the flue gas-side heat supply to the final evaporator can be provided, which can be brought about, for example, by flue gas circulation or through a shunt channel through which flue gases can be directed past the final evaporator.
  • the temperature difference can also be checked by a bypass line to the final evaporator 40 or, for example, by a temperature-controlled injection element in the area of the line 42.
  • the superheated steam flows out of the ring collector 55 through the second superheater 72, in which further heating takes place, and then via an injection element 74 in the line 73 through the final superheater 75.
  • a temperature measuring element (not shown) is provided on the subsequent live steam line 77 Control means not shown acts on the injection member 74.
  • the steam in the reheater 82 is reheated and fed to the low-pressure turbine 86, in which it is expanded to the vacuum generated in the condenser 1.
  • the delivery rate of the feed pump 16 is preferably kept constant for starting and in a load range below a certain limit load.
  • the outlet of the final evaporator 40 there is a load-dependent water content.
  • the water is separated in the separator 44 and returned to the feed water vessel 13 via the valve 46, which is controlled by the level in the separator 44.
  • a bypass line with throttle element parallel to the final evaporator 40, so that a partial flow of the working medium can be bypassed the final evaporator in the event of operation with high load.
  • the temperature difference between the tubes 27 and 53 in the region where they are welded to one another can thus be reduced, as a result of which the thermal stresses are reduced.
  • Thermal stresses in the areas of levels E and F can also be reduced by directly welding the tubes 27 and 53 to each other only over short lengths and the sealing being achieved by means of a skin construction.

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

Claims (3)

1. Installation à marche forcée génératrice de vapeur à chauffage par des combustibles fossiles, comportant les éléments constitutifs suivants, montés en série par rapport au flux du fluide de travail:
- une pompe d'alimentation (16) à haute pression
- un économiseur (20)
- un évaporateur (26) consistant en des tubes verticaux (27) soudés hermétiquement et formant des parois (29) de la chambre de combustion du générateur de vapeur
- un séparateur d'eau (44)
- plusieurs surfaces chaudes de surchauffeurs (53, 75, 72),

des tubes (53) formant la paroi de la première surface chaude de surchauffeur étant raccordés aux tubes verticaux (27) de l'évaporateur, ces tubes (53) étant soudés hermétiquement les uns aux autres et à ceux de l'évaporateur (26) et étant reliés au séparateur d'eau (44) dans les zones de raccordement (51), par l'intermédiaire de conduits (50) de sortie de la vapeur, caractérisée par le fait que la sortie d'eau du séparateur d'eau (44) est raccordée au flux du fluide de travail par l'intermédiaire d'un conduit de réintroduction (45), entre une installation (8) de traitement d'eau pour déminéraliser l'eau d'alimentation et la pompe d'alimentation (16) à haute pression, l'installation (8) de traitement d'eau étant conçue avec une conductivité de l'eau d'alimentation inférieure à 0,2 microsiemens/cm et une réduction de la teneur en silicium de l'eau d'alimentation inférieure à 0,02 ppm; et par le fait qu'il est prévu, dans le flux du fluide de travail, entre l'évaporateur (26) et le séparateur d'eau (44), un évaporateur final (40) qui est intercalé, dans le carneau (60) à gaz de combustion, entre la dernière surface chaude du surchauffeur (72) entourée de toutes parts par les gaz de carneau et l'économiseur (20).
2. Installation à marche forcée génératrice de vapeur selon la revendication 1, caractérisée par le fait que la surface chaude formant l'évaporateur final (40) et consistant en des tubes (41) est agrandie du côté des gaz par des nervures s'étendant de préférence dans le sens périphérique desdits tubes.
3. Installation à marche forcée génératrice de vapeur selon la revendication 1 ou 2, caractérisée par le fait que les tubes (27) de l'évaporateur formant les parois (29) de la chambre de combustion présentent, au moins dans la zone (A) de la plus forte action de la chaleur, des gorges internes de configuration hélicoïdale.
EP81100601A 1980-12-23 1981-01-28 Chaudière à vapeur à circulation forcée Expired - Lifetime EP0054601B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH949780 1980-12-23
CH9497/80 1980-12-23

Publications (3)

Publication Number Publication Date
EP0054601A1 EP0054601A1 (fr) 1982-06-30
EP0054601B1 true EP0054601B1 (fr) 1984-09-19
EP0054601B2 EP0054601B2 (fr) 1991-08-28

Family

ID=4352617

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81100601A Expired - Lifetime EP0054601B2 (fr) 1980-12-23 1981-01-28 Chaudière à vapeur à circulation forcée

Country Status (8)

Country Link
US (1) US4430962A (fr)
EP (1) EP0054601B2 (fr)
JP (1) JPS57117705A (fr)
AU (1) AU542220B2 (fr)
CA (1) CA1176517A (fr)
DE (1) DE3166099D1 (fr)
FI (1) FI68458C (fr)
YU (1) YU238181A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0104272A1 (fr) * 1982-09-17 1984-04-04 GebràœDer Sulzer Aktiengesellschaft Dispositif servomoteur actionné par fluide sous pression
EP0197378A1 (fr) * 1985-04-01 1986-10-15 Siemens Aktiengesellschaft Chaudière à vapeur à circulation ouverte
DE19504308C1 (de) * 1995-02-09 1996-08-08 Siemens Ag Verfahren und Vorrichtung zum Anfahren eines Durchlaufdampferzeugers
US6125634A (en) * 1992-09-30 2000-10-03 Siemens Aktiengesellschaft Power plant

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DE3447265A1 (de) * 1984-12-22 1986-06-26 L. & C. Steinmüller GmbH, 5270 Gummersbach Verfahren und vorrichtung zur erzeugung von hochgespanntem und ueberhitztem dampf
JPH0539282Y2 (fr) * 1985-01-29 1993-10-05
US4843824A (en) * 1986-03-10 1989-07-04 Dorothy P. Mushines System for converting heat to kinetic energy
US4896496A (en) * 1988-07-25 1990-01-30 Stone & Webster Engineering Corp. Single pressure steam bottoming cycle for gas turbines combined cycle
JP2516661B2 (ja) * 1988-07-25 1996-07-24 三菱重工業株式会社 再熱式排ガスボイラ
US5048466A (en) * 1990-11-15 1991-09-17 The Babcock & Wilcox Company Supercritical pressure boiler with separator and recirculating pump for cycling service
SE469606B (sv) * 1991-12-20 1993-08-02 Abb Carbon Ab Foerfarande vid start och laaglastdrift av genomstroemningspanna och anordning foer genomfoerande av foerfarandet
US5390631A (en) * 1994-05-25 1995-02-21 The Babcock & Wilcox Company Use of single-lead and multi-lead ribbed tubing for sliding pressure once-through boilers
DE19528438C2 (de) * 1995-08-02 1998-01-22 Siemens Ag Verfahren und System zum Anfahren eines Durchlaufdampferzeugers
US5713311A (en) * 1996-02-15 1998-02-03 Foster Wheeler Energy International, Inc. Hybrid steam generating system and method
US6675747B1 (en) * 2002-08-22 2004-01-13 Foster Wheeler Energy Corporation System for and method of generating steam for use in oil recovery processes
US20030167769A1 (en) * 2003-03-31 2003-09-11 Desikan Bharathan Mixed working fluid power system with incremental vapor generation
WO2005068905A1 (fr) * 2004-01-20 2005-07-28 Siemens Aktiengesellschaft Procede et dispositif de deflegmation dans un groupe-vapeur
US7093566B2 (en) * 2004-11-12 2006-08-22 Maxitherm Inc. Vapor generator
US7874140B2 (en) * 2007-06-08 2011-01-25 Foster Wheeler North America Corp. Method of and power plant for generating power by oxyfuel combustion
US7621237B2 (en) * 2007-08-21 2009-11-24 Hrst, Inc. Economizer for a steam generator
EP2182278A1 (fr) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Générateur de vapeur en continu
JP5054642B2 (ja) * 2008-09-09 2012-10-24 アクアインテック株式会社 管路補修システム
DE102010038883C5 (de) * 2010-08-04 2021-05-20 Siemens Energy Global GmbH & Co. KG Zwangdurchlaufdampferzeuger
EP2589760B1 (fr) * 2011-11-03 2020-07-29 General Electric Technology GmbH Centrale thermique à vapeur avec réservoir de chaleur haute température
KR101245088B1 (ko) * 2012-08-13 2013-03-18 서영호 전기로를 이용한 발전장치
DE102012217717A1 (de) * 2012-09-28 2014-04-03 Siemens Aktiengesellschaft Verfahren zur Rückgewinnung von Prozessabwässern einer Dampfkraftanlage
EP2746656A1 (fr) * 2012-12-19 2014-06-25 Siemens Aktiengesellschaft Drainage d'une centrale
ES2846148T3 (es) * 2015-04-21 2021-07-28 General Electric Technology Gmbh Generador de vapor de un solo paso de sal fundida
FI128782B (fi) * 2016-01-28 2020-12-15 Andritz Oy Talteenottokattilan lämmöntalteenottopintojen järjestely
CN109269138B (zh) * 2018-09-03 2020-10-30 南京天加环境科技有限公司 一种防止压缩机回液的多联机系统及其控制方法

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DE736611C (de) * 1940-10-01 1943-06-23 Duerrwerke Ag Zwangdurchlauf-Dampferzeuger mit einem unmittelbar an die Verdampfungsheizflaeche angeschlossenen UEberhitzer
DE1000828B (de) * 1954-04-30 1957-01-17 Siemens Ag Entsalzungseinrichtung fuer Zwangstrom-Dampferzeuger und Verfahren hierfuer
DE1015818B (de) * 1955-11-15 1957-09-19 Siemens Ag Zwangstrom-Dampferzeuger fuer sehr hohe Betriebsdruecke, insbesondere fuer ueberkritischen Druck
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CH477651A (de) * 1967-07-13 1969-08-31 Sulzer Ag Hochdruck-Zwangdurchlaufdampferzeugeranlage mit aus gasdicht geschweissten Rohren bestehender Brennkammer und Verfahren zum Betrieb der Anlage
US3789806A (en) * 1971-12-27 1974-02-05 Foster Wheeler Corp Furnace circuit for variable pressure once-through generator
US4191133A (en) * 1977-11-07 1980-03-04 Foster Wheeler Energy Corporation Vapor generating system utilizing integral separators and angularly arranged furnace boundary wall fluid flow tubes having rifled bores
JPS5472301A (en) * 1977-11-21 1979-06-09 Mitsubishi Heavy Ind Ltd Boiler
CH635184A5 (de) * 1978-12-22 1983-03-15 Sulzer Ag Dampferzeugeranlage.
US4290389A (en) * 1979-09-21 1981-09-22 Combustion Engineering, Inc. Once through sliding pressure steam generator

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0104272A1 (fr) * 1982-09-17 1984-04-04 GebràœDer Sulzer Aktiengesellschaft Dispositif servomoteur actionné par fluide sous pression
EP0197378A1 (fr) * 1985-04-01 1986-10-15 Siemens Aktiengesellschaft Chaudière à vapeur à circulation ouverte
US6125634A (en) * 1992-09-30 2000-10-03 Siemens Aktiengesellschaft Power plant
DE19504308C1 (de) * 1995-02-09 1996-08-08 Siemens Ag Verfahren und Vorrichtung zum Anfahren eines Durchlaufdampferzeugers
US5839396A (en) * 1995-02-09 1998-11-24 Siemens Aktiengesellschaft Method and apparatus for starting up a continuous-flow steam generator

Also Published As

Publication number Publication date
AU542220B2 (en) 1985-02-14
YU238181A (en) 1984-02-29
JPH0348402B2 (fr) 1991-07-24
FI813379L (fi) 1982-06-24
CA1176517A (fr) 1984-10-23
JPS57117705A (en) 1982-07-22
FI68458C (fi) 1985-09-10
FI68458B (fi) 1985-05-31
AU7836481A (en) 1982-07-01
EP0054601B2 (fr) 1991-08-28
DE3166099D1 (en) 1984-10-25
US4430962A (en) 1984-02-14
EP0054601A1 (fr) 1982-06-30

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