WO2010142495A2 - Évaporateur continu - Google Patents

Évaporateur continu Download PDF

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Publication number
WO2010142495A2
WO2010142495A2 PCT/EP2010/055886 EP2010055886W WO2010142495A2 WO 2010142495 A2 WO2010142495 A2 WO 2010142495A2 EP 2010055886 W EP2010055886 W EP 2010055886W WO 2010142495 A2 WO2010142495 A2 WO 2010142495A2
Authority
WO
WIPO (PCT)
Prior art keywords
steam generator
evaporator
tubes
continuous
inner profile
Prior art date
Application number
PCT/EP2010/055886
Other languages
German (de)
English (en)
Other versions
WO2010142495A3 (fr
Inventor
Jan BRÜCKNER
Joachim Franke
Original Assignee
Siemens Aktiengesellschaft
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 Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Priority to CA2764939A priority Critical patent/CA2764939A1/fr
Priority to CN201080025823XA priority patent/CN102667337A/zh
Priority to AU2010257702A priority patent/AU2010257702A1/en
Priority to JP2012514403A priority patent/JP2012529613A/ja
Priority to RU2011153331/06A priority patent/RU2011153331A/ru
Priority to EP10718147A priority patent/EP2440847A2/fr
Priority to BRPI1013116A priority patent/BRPI1013116A2/pt
Priority to US13/376,469 priority patent/US20120073520A1/en
Publication of WO2010142495A2 publication Critical patent/WO2010142495A2/fr
Publication of WO2010142495A3 publication Critical patent/WO2010142495A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F22B37/101—Tubes having fins or ribs
    • F22B37/103—Internally ribbed tubes
    • 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
    • F22B29/061—Construction of tube walls
    • F22B29/062—Construction of tube walls involving vertically-disposed water tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators

Definitions

  • the invention relates to a continuous evaporator for a heat recovery steam generator in lying construction with a first Verdampfersammlungflache comprising a number of substantially vertically arranged, from bottom to top flowed first steam generator tubes, and another, the first Verdampfersammlungflache flow medium side downstream second Verdampferiensflache, the Number of further, arranged substantially vertically, from bottom to top flowed through the second steam generator tubes.
  • 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 heat recovery steam generator connected downstream of the gas turbine, in which a number of heating surfaces for water preheating, steam generation and steam superheating is usually arranged.
  • the heating surfaces are connected in the water-steam cycle of the steam turbine.
  • the water-steam cycle usually includes several, z. B. three, pressure levels, each pressure stage may have a evaporator heating surface.
  • a continuous steam generator in contrast to a natural or forced circulation steam generator is not subject to pressure limitation.
  • a high live steam pressure promotes a high thermal efficiency and thus low CO 2 emissions of a fossil-fired power plant.
  • a continuous steam generator in comparison to a circulating steam generator has a simple design and can therefore be produced with particularly little effort.
  • the use of a designed according to the flow principle steam generator as heat recovery steam generator of a gas and steam turbine plant is therefore particularly favorable to achieve a high overall efficiency of the gas and steam turbine plant with a simple design.
  • a continuous steam generator designed as a heat recovery steam generator can in principle be embodied in one of two alternative designs, namely in upright design or in horizontal construction.
  • Construction is designed for a flow through the heated medium or heating gas, for example, the exhaust gas from the gas turbine, in approximately horizontal direction, whereas a continuous steam generator is designed in standing construction for a flow of the heated medium in an approximately vertical direction.
  • a continuous steam generator in lying construction is in contrast to a continuous steam generator in a stile construction with particularly simple means and with very low
  • the invention is therefore based on the object to provide a continuous evaporator for a heat recovery steam generator of the type mentioned above, which allows for a particularly long service life, a particularly simple design.
  • the invention is based on the consideration that a particularly simple construction of the heat recovery steam generator or of the continuous evaporator could be achieved by eliminating the usual expansion bends.
  • the mechanical stresses caused by temperature imbalances in the steam generator tubes of each individual row of tubes connected in parallel must be reduced in a different manner. These occur in particular in the second evaporator heating surface, which is acted upon by a water-steam mixture.
  • the temperature imbalances are caused by different proportions of water and steam at the flow-side inlet of the individual tubes of a row of tubes and a resulting different flow through these tubes. It has been recognized that this differential flow in the tubes is caused by a low friction pressure loss in the steam generator tubes compared to the geodetic pressure loss.
  • a flow with a high vapor content of the flow medium flows namely at low friction pressure loss comparatively quickly through individual steam generator tubes, while a flow with high water content is disadvantaged due to their higher, caused by the mass geodetic pressure loss and may tend to stagnation.
  • the friction pressure loss should be increased. This is achievable by adding a number of second steam generator tubes has an inner profile, which causes such additional friction pressure loss.
  • the laminar boundary layer on the inside of the tubes should be reduced. This can be achieved by generating turbulence in the pipe. This effect can be further enhanced by creating a twist of the flow medium. Such swirl generation is possible in which the inner profile is advantageously helical spring-shaped.
  • This friction pressure loss should be determined according to the other operating parameters such as the tube geometry, the dimensions of the heating gas channel and the temperature conditions.
  • the profile geometry of the respective inner profile should be chosen such that adjusts the predetermined friction pressure loss of the flow medium via the respective second steam generator tube.
  • the respective inner profile is introduced in the manner of a réelleberippung in the respective second steam generator tube. This allows a particularly simple construction of a continuous evaporator or a heat recovery steam generator.
  • the respective inner profile is advantageously used as a built-in part in the respective second steam generator tube.
  • the inner profile is thus configured as a separate built-in part and arranged in the steam generator tubes.
  • a number of second steam generator tubes each other on the heating gas side as rows of tubes connected in series is made it possible to use a larger number of steam generator tubes connected in parallel for an evaporator heating surface, which means a better heat input due to the increased surface area.
  • successively arranged steam generator tubes are heated differently. The flow medium is heated to a comparatively high degree, in particular in the heating gas inlet-side steam generator tubes. Due to the described embodiment of the second steam generator tubes with an inner profile, however, it is also possible to use them in these
  • the first evaporator heating surface of the second evaporator heating surface is connected downstream of the heating gas side. This offers the advantage that the second evaporator heating surface designed downstream of the flow medium side and thus already vaporized for further heating is also located in a comparatively more heated region of the heating gas channel.
  • such a continuous evaporator is used in a heat recovery steam generator and the heat recovery steam generator is used in a gas and steam turbine plant.
  • the steam generator is advantageously followed by a gas turbine on the hot gas side.
  • the advantages achieved by the invention are in particular that an improvement of the distribution of the flow and thus a reduction in the temperature differences between parallel connected second steam generator tubes and the resulting mechanical stresses is achieved by the introduction of an inner profile in the second evaporator tubes.
  • an inner profile in the second evaporator tubes.
  • the corresponding arrangement of an inner profile means that additional, complex technical measures such as expansion bends can be dispensed with and at the same time a particularly simple, cost-saving construction of the heat recovery steam generator or of a combined cycle gas turbine power plant is made possible.
  • FIG. 5 shows a graphic representation of the pipe temperature against the steam content at the heating pipe inlet with internal profile.
  • the continuous evaporator 1 for the heat recovery steam generator 2 GE measure of FIG 1 is downstream of a gas turbine not shown in detail on the exhaust side.
  • the heat recovery steam generator 2 has a surrounding wall 3, which forms a heating gas duct 5 for the exhaust gas from the gas turbine which can be flowed through in an approximately horizontal heating gas direction indicated by the arrows 4.
  • a number of designed according to the flow principle evaporator 8, 10 is arranged in the heating gas channel 5, a number of designed according to the flow principle evaporator 8, 10 is arranged.
  • two evaporator heating surfaces 8, 10 are shown, but it can also a larger number of Verdampferlikflachen be provided.
  • the evaporator heating surfaces 8, 10 according to FIG. 1 each comprise, in the manner of a tube bundle, a number of rows of tubes 11 or 12 arranged behind one another in the heating gas direction.
  • Each row of tubes 11, 12 in each case comprises a number of steam generator tubes 13 arranged side by side in the heating gas direction. 14, of which only one is visible for each row of tubes 11, 12.
  • the approximately vertically arranged, for the flow of a flow medium W connected in parallel first steam generator tubes 13 of the first evaporator 8 are connected on the output side to a common outlet collector 15.
  • Flow medium W parallel connected second steam generator tubes 14 of the second evaporator 10 are also connected on the output side to a common outlet collector 16.
  • a comparatively complex collector system can also be provided for both evaporator heating surfaces 8, 10.
  • the steam generator tubes 14 of the second evaporator heating surface 10 are downstream of the steam generator tubes 13 of the first evaporator heating surface 8 via a downflow system 17.
  • the evaporator system formed from the evaporator 8, 10 evaporator system can be acted upon with the flow medium W, which is vaporized in a single pass through the evaporator system and discharged after exiting the second Verdampfersammlungflache 10 as steam D.
  • the evaporator system formed from the evaporator 8, 10 evaporator system is connected in the not shown water-steam cycle of a steam turbine.
  • a number of other, in FIG 1 schematically indicated heating surfaces 20 are connected in the water-steam cycle of the steam turbine.
  • the heating surfaces 20 may be, for example, superheaters, medium pressure evaporator to act low pressure evaporator and / or preheater.
  • the second steam generator tubes 14 now have a helical spring-shaped inner profile 22, which is shown in FIGS. 2 and 3. Its profile geometry is selected such that the friction pressure loss of the flow medium W in the steam generator tubes 14, generated by swirl and turbulence, is correspondingly high enough to ensure uniform flow within a row of tubes 11. This reduces temperature imbalances.
  • the inner profile 22 can be introduced directly into the steam generator tubes 14 in the manner of an inner nip 23.
  • built-in parts 24 serve as an inner profile 22, which in particular allows retrofitting existing continuous evaporator 1.
  • FIGS. 4 and 5 show a graphical representation of the mean tube wall temperature 25 and the tube outlet wall temperature 27, plotted against the vapor fraction 29 of the flow medium at the inlet into the tube. 4 shows the situation without an inner profile 22.
  • the average tube wall temperature 25 varies between about 460 0 C and 360 ° C
  • the Rohrausbergswandtemperatur 27 between 480 0 C and 370 0 C, depending on the vapor content 29.
  • FIG 5 the Situation illustrated with inner profile 22, it is shown that reduce these variations to about 440 0 C to 390 0 C and 470 0 C to 405 ° C. The temperature differences between pipes with different steam content at the entrance are thus significantly reduced.

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  • 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)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)

Abstract

L'invention concerne un évaporateur continu (1) pour un générateur de vapeur à récupération de chaleur (2) de type horizontal. L'évaporateur continu selon l'invention comprend une première surface chauffante (8) qui présente un certain nombre de premiers tubes générateurs de vapeur (13) pratiquement verticaux dans lesquels l'écoulement se fait de bas en haut, ainsi qu'une deuxième surface chauffante (10) qui est placée en aval de la première surface chauffante (8) côté fluide d'écoulement et qui présente un certain nombre de deuxièmes tubes générateurs de vapeur (14) pratiquement verticaux dans lesquels l'écoulement se fait de bas en haut. L'invention vise à fournir un évaporateur continu de durée de vie particulièrement élevée pour une conception particulièrement simple. A cet effet, un certain nombre de deuxièmes tubes générateurs de vapeur (14) comportent un profil intérieur (22).
PCT/EP2010/055886 2009-06-10 2010-04-30 Évaporateur continu WO2010142495A2 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
CA2764939A CA2764939A1 (fr) 2009-06-10 2010-04-30 Evaporateur continu
CN201080025823XA CN102667337A (zh) 2009-06-10 2010-04-30 直流式蒸发器
AU2010257702A AU2010257702A1 (en) 2009-06-10 2010-04-30 Continuous evaporator
JP2012514403A JP2012529613A (ja) 2009-06-10 2010-04-30 貫流蒸発器
RU2011153331/06A RU2011153331A (ru) 2009-06-10 2010-04-30 Испаритель проточного типа
EP10718147A EP2440847A2 (fr) 2009-06-10 2010-04-30 Évaporateur continu
BRPI1013116A BRPI1013116A2 (pt) 2009-06-10 2010-04-30 evaporador contínuo
US13/376,469 US20120073520A1 (en) 2009-06-10 2010-04-30 Continuous evaporator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009024587A DE102009024587A1 (de) 2009-06-10 2009-06-10 Durchlaufverdampfer
DE102009024587.1 2009-06-10

Publications (2)

Publication Number Publication Date
WO2010142495A2 true WO2010142495A2 (fr) 2010-12-16
WO2010142495A3 WO2010142495A3 (fr) 2012-06-07

Family

ID=43069748

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/055886 WO2010142495A2 (fr) 2009-06-10 2010-04-30 Évaporateur continu

Country Status (12)

Country Link
US (1) US20120073520A1 (fr)
EP (1) EP2440847A2 (fr)
JP (1) JP2012529613A (fr)
KR (1) KR20120027021A (fr)
CN (1) CN102667337A (fr)
AU (1) AU2010257702A1 (fr)
BR (1) BRPI1013116A2 (fr)
CA (1) CA2764939A1 (fr)
DE (1) DE102009024587A1 (fr)
RU (1) RU2011153331A (fr)
TW (1) TW201043874A (fr)
WO (1) WO2010142495A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2390567A1 (fr) * 2010-05-31 2011-11-30 Siemens Aktiengesellschaft Dispositif de fabrication de corps d'insertion pour tuyaux de génération de vapeur

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2180250A1 (fr) * 2008-09-09 2010-04-28 Siemens Aktiengesellschaft Générateur de vapeur en continu
DE102013206014A1 (de) * 2013-04-05 2014-10-09 Dürr Systems GmbH Energiewandler-System und Baugruppen hierfür
CN105202509B (zh) * 2014-06-20 2019-05-31 松下知识产权经营株式会社 蒸发器、朗肯循环装置以及热电联供系统
CN108263904B (zh) * 2018-01-15 2020-04-14 芜湖航天特种电缆厂股份有限公司 预热线缆传输机
CN110094709B (zh) * 2019-05-28 2024-04-26 上海锅炉厂有限公司 一种直流式蒸发器及其设计方法

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JPS63189793A (ja) * 1987-02-02 1988-08-05 Mitsubishi Electric Corp 蒸発・凝縮用伝熱管
EP0349834B1 (fr) * 1988-07-04 1996-04-17 Siemens Aktiengesellschaft Chaudière à vapeur à passage unique
DE58909259D1 (de) * 1989-10-30 1995-06-29 Siemens Ag Durchlaufdampferzeuger.
DE4333404A1 (de) * 1993-09-30 1995-04-06 Siemens Ag Durchlaufdampferzeuger mit vertikal angeordneten Verdampferrohren
US5772793A (en) * 1996-08-28 1998-06-30 The United States Of America As Represented By The United States Department Of Energy Tube-in-tube thermophotovoltaic generator
DE19644763A1 (de) * 1996-10-28 1998-04-30 Siemens Ag Dampferzeugerrohr
DE19651678A1 (de) * 1996-12-12 1998-06-25 Siemens Ag Dampferzeuger
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JP2002507272A (ja) * 1997-06-30 2002-03-05 シーメンス アクチエンゲゼルシヤフト 廃熱ボイラ
US5924389A (en) * 1998-04-03 1999-07-20 Combustion Engineering, Inc. Heat recovery steam generator
DE19914760C1 (de) * 1999-03-31 2000-04-13 Siemens Ag Fossilbeheizter Durchlaufdampferzeuger
EP1288567A1 (fr) * 2001-08-31 2003-03-05 Siemens Aktiengesellschaft Générateur de vapeur et procédé de démarrage d'un générateur de vapeur ayant un canal de gas de chauffage, celui-ci étant traversé par le gas de chauffage avec une direction sensiblement horizontale
EP1443268A1 (fr) * 2003-01-31 2004-08-04 Siemens Aktiengesellschaft Générateur de vapeur
US6957630B1 (en) * 2005-03-31 2005-10-25 Alstom Technology Ltd Flexible assembly of once-through evaporation for horizontal heat recovery steam generator
EP1793163A1 (fr) * 2005-12-05 2007-06-06 Siemens Aktiengesellschaft Tube de générateur de vapeur, procédé de fabrication associé et chaudière à vapeur à passage unique
EP1793164A1 (fr) * 2005-12-05 2007-06-06 Siemens Aktiengesellschaft Tube de générateur de vapeur, procédé de fabrication associé et chaudière à vapeur à passage unique
EP2182278A1 (fr) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Générateur de vapeur en continu

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Title
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2390567A1 (fr) * 2010-05-31 2011-11-30 Siemens Aktiengesellschaft Dispositif de fabrication de corps d'insertion pour tuyaux de génération de vapeur
WO2011151135A3 (fr) * 2010-05-31 2012-10-11 Siemens Aktiengesellschaft Procédé de fabrication de tubes de générateur de vapeur

Also Published As

Publication number Publication date
KR20120027021A (ko) 2012-03-20
TW201043874A (en) 2010-12-16
CA2764939A1 (fr) 2010-12-16
RU2011153331A (ru) 2013-07-20
AU2010257702A1 (en) 2012-01-12
DE102009024587A1 (de) 2010-12-16
US20120073520A1 (en) 2012-03-29
WO2010142495A3 (fr) 2012-06-07
BRPI1013116A2 (pt) 2016-04-05
JP2012529613A (ja) 2012-11-22
CN102667337A (zh) 2012-09-12
EP2440847A2 (fr) 2012-04-18

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