EP0944801A1 - Chaudiere a vapeur - Google Patents

Chaudiere a vapeur

Info

Publication number
EP0944801A1
EP0944801A1 EP97951103A EP97951103A EP0944801A1 EP 0944801 A1 EP0944801 A1 EP 0944801A1 EP 97951103 A EP97951103 A EP 97951103A EP 97951103 A EP97951103 A EP 97951103A EP 0944801 A1 EP0944801 A1 EP 0944801A1
Authority
EP
European Patent Office
Prior art keywords
steam generator
heating surface
continuous heating
steam
tube
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
EP97951103A
Other languages
German (de)
English (en)
Other versions
EP0944801B1 (fr
Inventor
Eberhard Wittchow
Joachim Franke
Rudolf Kral
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7814473&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0944801(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP0944801A1 publication Critical patent/EP0944801A1/fr
Application granted granted Critical
Publication of EP0944801B1 publication Critical patent/EP0944801B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/12—Forms of water tubes, e.g. of varying cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/62—Component parts or details of steam boilers specially adapted for steam boilers of forced-flow type
    • F22B37/70—Arrangements for distributing water into water tubes
    • F22B37/74—Throttling arrangements for tubes or sets of tubes

Definitions

  • the invention relates to a steam generator.
  • the heat contained in the relaxed working fluid or heating gas from the gas turbine is used to generate steam for the steam turbine.
  • the heat transfer takes place in a waste heat steam generator connected downstream of the gas turbine, in which a number of heating surfaces for preheating water, for steam generation and for steam superheating are usually arranged.
  • the heating surfaces are connected to the water-steam cycle of the steam turbine.
  • the water-steam cycle usually comprises several, e.g. three, pressure levels, each pressure level 'can have an evaporator heating surface.
  • Design concepts namely the design as a continuous steam generator or the design as a circulation steam generator.
  • the heating of steam generator pipes provided as evaporator pipes leads to an evaporation of the flow medium in the steam generator pipes in a single pass.
  • the water circulating is only partially evaporated when it passes through the evaporator tubes. After the steam generated has been separated off, the water which has not evaporated is fed back to the same evaporator tubes for further evaporation.
  • a high live steam pressure favors a high thermal efficiency and thus low CO 2 emissions from a fossil-fired power plant.
  • a continuous steam generator has a simple construction in comparison to a circulation steam generator and can therefore be produced with particularly little effort.
  • the use of a steam generator designed according to the continuous flow principle as waste heat steam generator of a gas and steam turbine system is therefore particularly favorable in order to achieve a high overall efficiency of the gas and steam turbine system with a simple construction.
  • a continuous steam generator can basically be designed in one of two alternative designs, namely in a standing construction or in a lying construction.
  • a continuous steam generator in a horizontal design is designed to flow through the heating medium or heating gas, for example the exhaust gas from the gas turbine, in an approximately horizontal direction, whereas a continuous steam generator in a standing construction is designed to flow through the heating medium in an approximately vertical direction is designed.
  • a continuous steam generator in a horizontal design can be produced with particularly simple means and with particularly low manufacturing and assembly costs.
  • the steam generator tubes of a heating surface are exposed to a very different heating depending on their positioning.
  • different heating of individual steam generator tubes can, however, lead to a merging of steam flows with widely differing the steam parameters and thus to undesired losses in efficiency, in particular to a comparatively reduced effectiveness of the heating surface concerned and thus reduced steam generation.
  • Different heating of adjacent steam generator tubes can also lead to damage to the steam generator tubes or the collector, particularly in the area where they flow into an outlet header.
  • the invention has for its object to provide a steam generator that is suitable for a horizontal design and also has the advantages of a continuous steam generator.
  • the steam generator should continue to enable a particularly high efficiency of a fossil-fired power plant.
  • a steam generator in which at least one continuous heating surface is arranged in a heating gas channel through which the heating gas can flow in an approximately horizontal direction, which is formed from a number of approximately vertically arranged steam generator pipes connected in parallel to the flow of a flow medium, and which is designed in this way that in comparison to another steam generator tube of the same continuous heating surface, a more heated steam generator tube has a higher throughput of the flow medium compared to the other steam generator tube.
  • a continuous heating surface is to be understood as a heating surface which is designed according to the continuous principle.
  • the flow medium supplied to the continuous heating surface is thus completely evaporated in a single pass through the continuous heating surface or through a heating surface system comprising a plurality of continuous heating surfaces connected in series.
  • a continuous heating surface of such a heating surface chensystems can also be provided for preheating or overheating the flow medium.
  • the or each continuous heating surface in particular in the manner of a tube bundle, can comprise a number of tube layers arranged one behind the other in the heating gas direction, each of which is formed from a number of steam generator tubes arranged side by side in the heating gas direction.
  • the invention is based on the consideration that in the case of a steam generator suitable for execution in a horizontal construction, the effect of locally different heating on the steam parameters should be kept particularly low for a high degree of efficiency.
  • the medium flowing through the steam generator pipes should have approximately the same temperature and / or the same steam content for each steam generator pipe assigned to a common continuous heating surface after it has left the steam generator pipes.
  • the steam generator tubes are advantageously at least one continuous heating surface on average for a ratio of Frictional pressure loss to geodetic pressure drop at full load of less than 0.4, preferably less than 0.2, designed or dimensioned.
  • the steam generator tubes are advantageously at least one pass-through heating surface of this pressure level on average for a ratio of frictional pressure loss to geodetic pressure drop at full load of less than 0.6, preferably less than 0.4, designed. This is based on the finding that different heating of two steam generator tubes then leads to particularly small temperature differences and / or differences in the steam content of the flow medium at the outputs of the respective steam generator tubes if an additional heating of a steam generator tube due to its design leads to an increase in the throughput of the flow medium in this steam generator pipe.
  • the geodetic pressure drop indicates the pressure drop due to the weight of the water and steam column in relation to the area of the flow cross-section in the steam generator tube.
  • the friction pressure loss describes the pressure drop in the steam generator tube due to the flow resistance for the flow medium.
  • the total pressure drop in a steam generator tube essentially consists of the geodetic pressure drop and the friction pressure loss.
  • a steam generator tube which is more heated in comparison to the steam generator tubes connected in parallel has an increased throughput of flow medium
  • a steam generator tube which is particularly slightly heated in comparison with the steam generator tubes connected in parallel has a particularly low throughput of flow medium.
  • the automatic increase in the throughput of flow medium desired by the design criterion mentioned for the steam generator tubes also occurs in a pressure range above the critical pressure of the flow medium when the steam generator tube is heated more than once.
  • the desired automatic increase in throughput in the event of multiple heating of a steam generator tube also occurs in a continuous heating surface which, in the design case, receives a water / steam mixture, even if the friction pressure loss in the steam generator tube is on average about five times higher than that of one Steam generator tube of a once-through heating surface, which in the design case only receives water.
  • Each steam generator tube of a once-through heating surface is expediently designed for a higher throughput of the flow medium than any steam generator tube of the same once through heating surface, as seen in the direction of the heating gas.
  • a steam generator tube of the or each continuous heating surface has a larger inner diameter than a steam generator tube of the same continuous heating surface arranged downstream of it in the direction of the heating gas. This ensures in a particularly simple manner that the steam generator tubes have a comparatively high throughput of flow medium in the region of comparatively high heating gas temperature.
  • a throttle device is connected upstream of a number of steam generator tubes of the or each continuous heating surface in the flow direction of the flow medium. In this case, especially in the design case, compared to steam generator tubes of the same continuous heating surface, less heated steam generator tubes can be provided with the throttle device. The throughput of the steam generator tubes of a continuous heating surface can thus be controlled, so that an additional adaptation of the throughput to the heating is made possible.
  • a throttle device can also be arranged upstream of the steam generator tubes in groups.
  • the or each continuous heating surface is assigned a plurality of inlet collectors and / or a plurality of outlet collectors, each inlet collector being connected upstream of a number of steam generator tubes of the respective continuous heating surface or each Outlet collector of a number of steam generator pipes of the respective flow heating surface is connected downstream.
  • a particularly favorable spatial arrangement of the steam generator tubes in their connection area to the inlet headers is thus possible.
  • each steam generator tube expediently have ribbing on the outside.
  • each steam generator tube can expediently be provided on its inner wall with a thread-like ribbing in order to increase the heat transfer from the steam generator tube to the flow medium flowing in it.
  • the steam generator is expediently used as a waste heat steam generator in a gas and steam turbine plant.
  • the steam generator is advantageously one on the hot gas side Downstream gas turbine.
  • an additional firing can advantageously be arranged behind the gas turbine to increase the heating gas temperature.
  • a steam generator which is particularly favorable for achieving a particularly high overall efficiency of a gas and steam turbine system can also be constructed horizontally and thus with particularly low manufacturing and assembly outlay. Material damage to the steam generator due to the particularly inhomogeneous spatially inhomogeneous heating of the steam generator pipes in this construction is reliably avoided due to the fluidic design of the steam generator.
  • Figures 1, 2 and 3 each in a simplified representation in longitudinal section of a steam generator in a horizontal design.
  • the steam generator 1 according to FIGS. 1, 2 and 3 is connected in the manner of a waste heat steam generator downstream of a gas turbine, not shown.
  • the steam generator 1 has a peripheral wall 2, which has a heating gas channel 3 for the exhaust gas from the exhaust gas which can flow through in an approximately horizontal heating gas direction indicated by the arrows 4
  • Forms gas turbine In the heating gas channel 3, a number of heating surfaces designed according to the continuous principle, also referred to as continuous heating surfaces 8, 10, are arranged. In the exemplary embodiment according to FIGS. 1, 2 and 3, two continuous heating surfaces 8, 10 are shown, but it can also only be a continuous heating surface or a larger number of continuous heating surfaces can be provided.
  • the continuous heating surfaces 8, 10 according to FIGS. 1, 2 and 3 each comprise, in the manner of a tube bundle, a number of tube layers 11 or 12 arranged one behind the other in the heating gas direction.
  • Each tube layer 11, 12 in turn comprises a number of steam generator tubes 13 arranged side by side in the heating gas direction or 14, of which only one is visible for each tube layer 11, 12.
  • the approximately vertically arranged steam generator tubes 13 of the first continuous heating surface 8, which are connected in parallel to flow through a flow medium W, are connected on the output side to an outlet header 15 common to them.
  • the steam generator tubes 14 of the second continuous heating surface 10 are the steam generator tubes 13 of the first
  • Flow heating surface 8 connected downstream in terms of flow technology via a downpipe system 17.
  • the evaporator system formed from the once-through heating surfaces 8, 10 can be acted upon by the flow medium W, which evaporates once through the evaporator system and is discharged as steam D after exiting the second once-through heating surface 10.
  • the evaporator system formed from the continuous heating surfaces 8, 10 is connected to the water-steam circuit of a steam turbine (not shown in more detail).
  • a number of further heating surfaces 20, schematically indicated in FIGS. 1, 2 and 3 are connected in the water-steam circuit of the steam turbine.
  • the heating surfaces 20 can be superheaters, for example Medium pressure evaporators, low pressure evaporators and / or preheaters.
  • the continuous heating surfaces 8, 10 are designed in such a way that local differences in the heating of the steam generator tubes 13 and 14 lead only to slight temperature differences or differences in the steam content in the flow medium W emerging from the respective steam generator tubes 13 and 14.
  • Each steam generator tube 13, 14 has a higher throughput of the flow medium W as a result of the design of the respective continuous heating surface 8, 10 than any steam generator tube 13 or 14 of the same continuous heating surface 8 or 10 seen in the heating gas direction.
  • the steam generator tubes 13 of the first continuous heating surface 8, which are connected on the input side to an inlet header 21, are designed in such a way that the ratio of frictional pressure loss to geodetic pressure drop within the respective steam generator tube 13 im during full-load operation of the steam generator 1
  • each steam generator tube 13, 14 of the continuous heating surface 8 or 10 can have a larger inner diameter than any steam generator tube 13 or 14 thereof arranged downstream of it in the direction of the heating gas
  • each steam generator tube 13, 14 of the continuous heating surfaces 8 and 10 is used to set a throughput adapted to the respective heating in the direction of flow of the flow medium W, a valve upstream as a throttle device 23.
  • the adaptation of the throughput of the steam generator tubes 13, 14 of the continuous heating surfaces 8, 10 to their different heating is supported in this way.
  • each continuous heating surface 8, 10 is assigned a plurality of inlet collectors 26 and 28 and a plurality of outlet collectors 30 and 32, respectively, which makes it possible to form groups in a particularly simple manner.
  • Each inlet header 26, 28 is connected upstream of a number of steam generator tubes 13 and 14 of the respective continuous heating surface 8 and 10 in the flow direction of the flow medium W.
  • each outlet collector 30, 32 is connected downstream in the flow direction of the flow medium W to a number of steam generator tubes 13 or 14 of the respective continuous heating surface 8 or 10.
  • the steam generator tubes 13, 14 of the once-through heating surfaces 8 and 10 are again designed such that when the steam generator 1 is in operation, the ratio of frictional pressure loss to geodetic pressure drop in the respective steam generator tube 13, 14 is on average less than 0.2 or 0.4.
  • a throttle device 34 is connected upstream of the tube groups thus formed.
  • the continuous steam generator 1 is adapted in terms of the design of its continuous heating surfaces 8, 10 to the spatially inhomogeneous heating of the steam generator tubes 13, 14 due to the horizontal design.
  • the steam generator 1 is therefore particularly suitable for a horizontal construction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Drying Of Solid Materials (AREA)
  • Pipe Accessories (AREA)

Abstract

L'invention a pour objet une chaudière (1) adaptée à une construction horizontale tout en offrant les avantages d'une chaudière continue. Pour ce faire, au moins une surface chauffante continue (8, 10) est disposée dans un canal où le gaz chaud circule dans une direction sensiblement horizontale. Cette surface chauffante continue est formée d'une pluralité de tubes (13, 14) parallèles et sensiblement verticaux servant à faire circuler un fluide. Elle est conçue de telle manière que le fluide parcourant un tube (13, 14) chauffé à une température supérieure à celle du tube (13, 14) suivant de la même surface chauffante continue (8, 10) ait un débit plus élevé que le fluide parcourant le tube (13, 14) suivant.
EP97951103A 1996-12-12 1997-12-01 Chaudiere a vapeur Expired - Lifetime EP0944801B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19651678 1996-12-12
DE19651678A DE19651678A1 (de) 1996-12-12 1996-12-12 Dampferzeuger
PCT/DE1997/002800 WO1998026213A1 (fr) 1996-12-12 1997-12-01 Chaudiere a vapeur

Publications (2)

Publication Number Publication Date
EP0944801A1 true EP0944801A1 (fr) 1999-09-29
EP0944801B1 EP0944801B1 (fr) 2001-02-21

Family

ID=7814473

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97951103A Expired - Lifetime EP0944801B1 (fr) 1996-12-12 1997-12-01 Chaudiere a vapeur

Country Status (10)

Country Link
US (1) US6189491B1 (fr)
EP (1) EP0944801B1 (fr)
JP (1) JP2001505645A (fr)
KR (1) KR100591469B1 (fr)
CN (1) CN1126903C (fr)
CA (1) CA2274656C (fr)
DE (2) DE19651678A1 (fr)
DK (1) DK0944801T3 (fr)
ES (1) ES2154914T3 (fr)
WO (1) WO1998026213A1 (fr)

Cited By (1)

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EP1443268A1 (fr) * 2003-01-31 2004-08-04 Siemens Aktiengesellschaft Générateur de vapeur

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EP1398564A1 (fr) 2002-09-10 2004-03-17 Siemens Aktiengesellschaft Procédé pour faire fonctionner un générateur de vapeur à construcion horizontale, et générateur de vapeur pour mettre en oeuvre ledit procédé
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US7878157B2 (en) * 2004-09-23 2011-02-01 Siemens Aktiengesellschaft Fossil-fuel heated continuous steam generator
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US6957630B1 (en) * 2005-03-31 2005-10-25 Alstom Technology Ltd Flexible assembly of once-through evaporation for horizontal heat recovery steam generator
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DE102009012322B4 (de) * 2009-03-09 2017-05-18 Siemens Aktiengesellschaft Durchlaufverdampfer
DE102009012321A1 (de) * 2009-03-09 2010-09-16 Siemens Aktiengesellschaft Durchlaufverdampfer
CN101539287B (zh) 2009-05-06 2011-01-05 清华大学 一种蒸汽发生器
DE102009024587A1 (de) * 2009-06-10 2010-12-16 Siemens Aktiengesellschaft Durchlaufverdampfer
NL2003596C2 (en) 2009-10-06 2011-04-07 Nem Bv Cascading once through evaporator.
US9273865B2 (en) 2010-03-31 2016-03-01 Alstom Technology Ltd Once-through vertical evaporators for wide range of operating temperatures
DE102010028720A1 (de) * 2010-05-07 2011-11-10 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Dampferzeugers
GB201010038D0 (en) 2010-06-16 2010-07-21 Doosan Power Systems Ltd Steam generator
DE102010038883C5 (de) 2010-08-04 2021-05-20 Siemens Energy Global GmbH & Co. KG Zwangdurchlaufdampferzeuger
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MX349702B (es) 2012-01-17 2017-08-08 General Electric Technology Gmbh Un método y aparato para conectar secciones de un evaporador horizontal directo.
US10274192B2 (en) 2012-01-17 2019-04-30 General Electric Technology Gmbh Tube arrangement in a once-through horizontal evaporator
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* Cited by examiner, † Cited by third party
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EP1443268A1 (fr) * 2003-01-31 2004-08-04 Siemens Aktiengesellschaft Générateur de vapeur
WO2004068032A1 (fr) * 2003-01-31 2004-08-12 Siemens Aktiengesellschaft Generateur de vapeur
AU2003288240B2 (en) * 2003-01-31 2009-04-23 Siemens Aktiengesellschaft Steam generator

Also Published As

Publication number Publication date
US6189491B1 (en) 2001-02-20
CN1126903C (zh) 2003-11-05
ES2154914T3 (es) 2001-04-16
DE19651678A1 (de) 1998-06-25
KR100591469B1 (ko) 2006-06-20
EP0944801B1 (fr) 2001-02-21
CA2274656C (fr) 2007-02-13
JP2001505645A (ja) 2001-04-24
WO1998026213A1 (fr) 1998-06-18
CN1239540A (zh) 1999-12-22
DE59703022D1 (de) 2001-03-29
KR20000057541A (ko) 2000-09-25
CA2274656A1 (fr) 1998-06-18
DK0944801T3 (da) 2001-06-11

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