EP2180251A1 - Durchlaufdampferzeuger - Google Patents

Durchlaufdampferzeuger Download PDF

Info

Publication number
EP2180251A1
EP2180251A1 EP08015863A EP08015863A EP2180251A1 EP 2180251 A1 EP2180251 A1 EP 2180251A1 EP 08015863 A EP08015863 A EP 08015863A EP 08015863 A EP08015863 A EP 08015863A EP 2180251 A1 EP2180251 A1 EP 2180251A1
Authority
EP
European Patent Office
Prior art keywords
tubes
combustion chamber
steam generator
gas
evaporator
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.)
Withdrawn
Application number
EP08015863A
Other languages
German (de)
English (en)
French (fr)
Inventor
Martin Effert
Joachim Dr. Franke
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP08015863A priority Critical patent/EP2180251A1/de
Priority to DK09782426.2T priority patent/DK2324286T3/da
Priority to JP2011525521A priority patent/JP5225469B2/ja
Priority to CN200980135065.4A priority patent/CN102149968B/zh
Priority to AU2009290998A priority patent/AU2009290998B2/en
Priority to EP09782426.2A priority patent/EP2324286B1/de
Priority to PL09782426T priority patent/PL2324286T3/pl
Priority to US13/062,704 priority patent/US20110203536A1/en
Priority to PCT/EP2009/061239 priority patent/WO2010028978A2/de
Publication of EP2180251A1 publication Critical patent/EP2180251A1/de
Withdrawn legal-status Critical Current

Links

Images

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
    • F22B29/08—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 fixed point of final state of complete evaporation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B19/00—Water-tube boilers of combined horizontally-inclined type and vertical type, i.e. water-tube boilers of horizontally-inclined type having auxiliary water-tube sets in vertical or substantially vertical arrangement
    • 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
    • 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
    • F22B29/067—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 at critical or supercritical pressure

Definitions

  • the invention relates to a continuous steam generator having a combustion chamber with a number of burners for fossil fuel, the heating gas side in a top region via a horizontal gas is followed by a vertical gas train, the Um chargedswand the combustion chamber in a lower region of gas-tight welded together, a Wasserabscheidesystem flow medium side upstream evaporator tubes and in an upper region of gas-tight welded together, the Wasserabscheidesystem flow medium side downstream superheater tubes is formed.
  • a fossil-fueled steam generator the energy of a fossil fuel is used to generate superheated steam, which can then be supplied to power a steam turbine, for example, in a power plant.
  • steam temperatures and pressures steam generators are usually designed as a water tube boiler, d. h., The supplied water flows in a number of tubes which receive the energy in the form of radiant heat of the burner flames and / or by convection of the resulting during combustion flue gas.
  • the steam generator tubes usually form the combustion chamber wall by being welded together in gas-tight fashion.
  • the combustion chamber downstream side of the combustion chamber arranged Dampfampfererrohe can be provided in the exhaust duct.
  • Fossil fueled steam generators can be categorized by a variety of criteria: Steam generators may generally be designed as natural, forced circulation or continuous flow steam generators. In a continuous steam generator, the heating of a number of evaporator tubes leads to a complete Evaporation of the flow medium in the evaporator tubes in one go.
  • the flow medium - usually water - is supplied to the evaporator tubes downstream superheater tubes after its evaporation and overheated there.
  • this description is only valid for partial loads with subcritical pressure of water (P Kri ⁇ 221 bar) - where at no temperature water and steam can occur simultaneously and thus no phase separation is possible - valid in the evaporator. For the sake of clarity, however, this illustration will be used throughout the following description.
  • the position of the evaporation end point ie the location at which the water content of the flow is completely evaporated, is variable and mode-dependent.
  • the evaporation end point is, for example, in an end region of the evaporator tubes, so that the overheating of the evaporated flow medium already begins in the evaporator tubes.
  • a continuous steam generator In contrast to a natural or forced circulation steam generator, a continuous steam generator is not subject to any pressure limitation, so that it can be designed for live steam pressures far above the critical pressure of water.
  • such a continuous steam generator is usually operated with a minimum flow of flow medium in the evaporator tubes in order to ensure reliable cooling of the evaporator tubes.
  • the pure mass flow through the evaporator usually no longer suffices for cooling the evaporator tubes, so that an additional throughput of flow medium is superimposed on the passage of flow medium through the evaporator in circulation.
  • the operationally provided minimum flow of flow medium in the evaporator tubes is thus not completely evaporated during startup or during low load operation in the evaporator tubes, so that in such an operating mode at the end of the evaporator tubes still unevaporated flow medium, in particular a water-vapor mixture, is present.
  • the evaporator tubes of the continuous steam generator are usually designed for a flow through unvaporised flow medium after passing through the combustion chamber walls, continuous steam generators are usually designed so that even when starting and in low load operation, a water ingress into the superheater tubes is reliably avoided.
  • the evaporator tubes are usually connected to the superheater tubes connected downstream via a Wasserabscheidesystem.
  • the water separator causes a separation of the emerging during the start or in low load operation of the evaporator tubes water-steam mixture in water and in steam.
  • the steam is supplied to the water separator downstream superheater tubes, whereas the separated water can be fed back to the evaporator tubes, for example via a circulating pump or discharged through a decompressor.
  • steam generators may continue to be classified, for example, into vertical and horizontal types.
  • a draw-in and two-pass boiler are distinguished.
  • the flue gas produced by the combustion in the combustion chamber always flows vertically from bottom to top. All arranged in the flue gas heating surfaces are flue gas side above the combustion chamber. Tower boilers offer a comparatively simple construction and easy control of the stresses caused by the thermal expansion of the tubes. Furthermore, all heating surfaces of the arranged in the flue gas duct steam generator tubes are horizontal and therefore completely drainable, which may be desirable in frost-prone environments.
  • a steam generator designed as a two-pass boiler usually the walls of the first draft, i. H. the combustion chamber completely switched as an evaporator.
  • the evaporator tubes flow medium side downstream Wasserabscheidesystem is accordingly arranged at the upper end of the combustion chamber.
  • the evaporator heating surfaces must be sufficiently cooled over the entire load range of the steam generator.
  • the mass flow required for cooling must be safely supplied to each individual tube.
  • the occurring stresses due to the thermal expansion of the individual pipes between adjacent pipes must not exceed the permissible values.
  • the temperatures of the flow medium are to be limited both in the absolute height and in the difference to the adjacent tubes, otherwise damage to the combustion chamber walls could arise.
  • mixing points can be used in the combustion chamber walls connected as evaporators.
  • the flow medium is discharged from the evaporator tubes, mixed and redistributed to the other evaporator tubes.
  • Such a system must be designed behind the mixing point for a uniform distribution of a water and vapor mixture.
  • Such a construction is accordingly technically complex and brings a significant increase in manufacturing costs.
  • the invention is therefore based on the object to provide a continuous steam generator of the type mentioned above, which has a particularly long life in a relatively simple construction.
  • This object is achieved according to the invention in that the boundary between the regions of the evaporator tubes and the superheater tubes is arranged essentially horizontally around the combustion chamber in the region of the bottom of the horizontal gas flue.
  • the invention is based on the consideration that a comparatively long service life would be achievable with a simultaneously simple construction if comparatively low temperature imbalances in the steam generator tubes could be achieved without arranging an additional mixing point in the evaporator tubes.
  • the water separator system present in the steam generator also collects the water leaving the evaporator tubes in circulation operation and separates it from the steam. In continuous operation, the incoming steam is mixed and distributed to the flow medium side downstream superheater tubes. At the same time, temperature imbalances are considerably reduced. Based on the knowledge that the water separation system thus fundamentally fulfills the function of a mixing point, it can thus be used as a mixing point within the combustion chamber wall by lowering it, for example into the region of the bottom of the horizontal gas flue, without the need for an additional mixing system.
  • this position of the water separation system ensures that the boundary between the regions of the evaporator tubes and the superheater tubes is arranged substantially horizontally around the combustion chamber in the region of the bottom of the horizontal gas flue.
  • the boundary between the regions of the evaporator tubes and the superheater tubes is arranged substantially horizontally around the combustion chamber at the height of the edge formed by the surrounding wall and bottom of the horizontal gas flue.
  • all welded to the tubes of the walls of the horizontal gas flue tubes of the combustion chamber are also designed as superheater tubes.
  • evaporator and superheater tubes were welded in parallel at this point. This is particularly problematic when hot starting the steam generator, as occur by filling the evaporator tubes with cold flow medium significant temperature differences to the unfilled superheater tubes.
  • the Wasserabscheidesystems in the height of the edge formed by the combustion chamber wall and the bottom of the horizontal gas flue occurs such a vertical separation point no longer and it is an overall safer operation of the steam generator at the same time comparatively long life achieved.
  • In Zweizugdampferzeugern may be inclined inwardly to the improvement of the gas flow facing the vertical gas part of the Um chargedswand below the horizontal gas and thus form a projecting into the combustion chamber nose with the bottom of the adjacent horizontal gas.
  • the boundary between the regions of the evaporator tubes and the superheater tubes is advantageously arranged substantially horizontally around the combustion chamber directly above the nose.
  • the bottom of the horizontal gas flue is gas-tight welded together, the Wasserabscheidesystem flow medium side upstream evaporator tubes formed.
  • the bottom of the horizontal gas flue is in fact suitable for being designed as an additional evaporator heating surface, since its tubes are not welded parallel to the vertically bored, connected as superheater walls of the horizontal gas flue and therefore the stresses remain relatively low due to the different thermal expansion.
  • the advantages associated with the invention are in particular that by the arrangement of the boundary between the areas of the evaporator tubes and the superheater tubes substantially horizontally surrounding the combustion chamber in the region of the bottom of the horizontal gas flue double use of Wasserabscheidesystems as a mixing point to reduce temperature differences between parallel Pipes becomes possible. Furthermore, one of the main drawbacks in Zweizugkessel, namely the vertical separation point between Wandsammlung vom, which are connected as evaporators and those that are connected as a superheater eliminated. This can be achieved by avoiding such voltages, a total safer operation and a longer life of the steam generator especially at the hot start of the steam generator, in which occur at this separation point high temperature differences and voltages when filling the evaporator tubes with comparatively cold flow medium.
  • FIG. 1 An embodiment of the invention is explained in more detail with reference to a drawing.
  • the figure shows a continuous steam generator in Zweizugbauweise in a schematic representation.
  • the continuous steam generator 1 according to the figure comprises a combustion chamber 2 designed as a vertical gas train, which is followed by a horizontal gas train 6 in an upper region 4. At the horizontal gas train 6, another vertical gas train 8 connects.
  • a number not shown burner is provided which burn a liquid or solid fuel in the combustion chamber.
  • the surrounding wall 12 of the combustion chamber 2 is formed from steam generator tubes which are welded together in a gastight manner and into which a flow medium, usually water, is pumped in by a pump (not shown in greater detail), which is heated by the heat generated by the burners.
  • the steam generator tubes can be aligned either spirally or vertically. In a helical arrangement, a comparatively higher design effort is required, but the resulting imbalances between parallel connected pipes are comparatively lower than in the case of a perpendicularly annealed combustion chamber 2.
  • the steam generator tubes in the lower part 10 of the combustion chamber 2 are designed as evaporator tubes.
  • the flow medium is first evaporated in them and fed via pipes 14 to a Wasserabscheidesystem not shown in detail.
  • not yet evaporated water is collected and removed.
  • the generated steam is conducted into the walls of the combustion chamber 2 and distributed to the superheater tubes arranged in the upper region 4 and in the walls of the horizontal gas flue 6.
  • Such a separation not yet evaporated water is necessary in particular during start-up operation, if for safe cooling of the evaporator tubes larger amount of flow medium must be pumped, as can be evaporated in an evaporator tube run.
  • the continuous steam generator 1 shown further comprises for improving the flue gas duct a nose 16, which merges directly into the bottom 18 of the horizontal gas flue 6 and projects into the combustion chamber 2. Furthermore, a grid 20 is arranged from further superheater tubes in the transition region from the combustion chamber 2 to the horizontal gas flue 6 in the flue gas duct.
  • the boundary 22 between evaporator tubes and superheater tubes at the level of the bottom 18 of the horizontal gas flue 6 is located directly above the nose 16.
  • the Wasserabscheidesystem not only acts as a separator in the start-up but also in continuous operation as a mixing point, since in the Wasserabscheidesystem the entire flow medium collected from the evaporator tubes, mixed and redistributed to the superheater tubes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
EP08015863A 2008-09-09 2008-09-09 Durchlaufdampferzeuger Withdrawn EP2180251A1 (de)

Priority Applications (9)

Application Number Priority Date Filing Date Title
EP08015863A EP2180251A1 (de) 2008-09-09 2008-09-09 Durchlaufdampferzeuger
DK09782426.2T DK2324286T3 (da) 2008-09-09 2009-09-01 Gennemløbsdampgenerator
JP2011525521A JP5225469B2 (ja) 2008-09-09 2009-09-01 貫流ボイラ
CN200980135065.4A CN102149968B (zh) 2008-09-09 2009-09-01 直流式锅炉
AU2009290998A AU2009290998B2 (en) 2008-09-09 2009-09-01 Continuous steam generator
EP09782426.2A EP2324286B1 (de) 2008-09-09 2009-09-01 Durchlaufdampferzeuger
PL09782426T PL2324286T3 (pl) 2008-09-09 2009-09-01 Przepływowa przetwornica pary
US13/062,704 US20110203536A1 (en) 2008-09-09 2009-09-01 Continuous steam generator
PCT/EP2009/061239 WO2010028978A2 (de) 2008-09-09 2009-09-01 Durchlaufdampferzeuger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08015863A EP2180251A1 (de) 2008-09-09 2008-09-09 Durchlaufdampferzeuger

Publications (1)

Publication Number Publication Date
EP2180251A1 true EP2180251A1 (de) 2010-04-28

Family

ID=41796032

Family Applications (2)

Application Number Title Priority Date Filing Date
EP08015863A Withdrawn EP2180251A1 (de) 2008-09-09 2008-09-09 Durchlaufdampferzeuger
EP09782426.2A Active EP2324286B1 (de) 2008-09-09 2009-09-01 Durchlaufdampferzeuger

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP09782426.2A Active EP2324286B1 (de) 2008-09-09 2009-09-01 Durchlaufdampferzeuger

Country Status (8)

Country Link
US (1) US20110203536A1 (zh)
EP (2) EP2180251A1 (zh)
JP (1) JP5225469B2 (zh)
CN (1) CN102149968B (zh)
AU (1) AU2009290998B2 (zh)
DK (1) DK2324286T3 (zh)
PL (1) PL2324286T3 (zh)
WO (1) WO2010028978A2 (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2182278A1 (de) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Durchlaufdampferzeuger
EP2213936A1 (de) * 2008-11-10 2010-08-04 Siemens Aktiengesellschaft Durchlaufdampferzeuger
DE102013215457A1 (de) * 2013-08-06 2015-02-12 Siemens Aktiengesellschaft Durchlaufdampferzeuger in Zweizugkesselbauweise
US10429062B2 (en) * 2016-04-05 2019-10-01 The Babcock & Wilcox Company High temperature sub-critical boiler with steam cooled upper furnace
US10415819B2 (en) * 2016-04-05 2019-09-17 The Babcock & Wilcox Company High temperature sub-critical boiler with common steam cooled wall between furnace and convection pass

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3288117A (en) * 1965-12-01 1966-11-29 Combustion Eng Arrangement of tube circuits in supercritical forced through-flow vapor generator
EP0308728A1 (de) * 1987-09-21 1989-03-29 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Durchlaufdampferzeugers
US5787844A (en) * 1995-03-06 1998-08-04 Ahlstrom Machinery Oy Economizer system
DE19717158A1 (de) * 1997-04-23 1998-11-05 Siemens Ag Durchlaufdampferzeuger und Verfahren zum Anfahren eines Durchlaufdampferzeugers
EP0884526A1 (en) * 1996-12-17 1998-12-16 Babcock-Hitachi Kabushiki Kaisha Boiler
EP1188986A2 (en) * 2000-09-18 2002-03-20 Kvaerner Pulping Oy Arrangement in recovery boiler

Family Cites Families (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2170345A (en) * 1935-12-18 1939-08-22 Babcock & Wilcox Co Vapor generator
US2087801A (en) * 1937-03-23 1937-07-20 Babcock & Wilcox Co Furnace
US2231872A (en) * 1937-04-16 1941-02-18 Babcock & Wilcox Co Radiant boiler
US2579559A (en) * 1946-12-19 1951-12-25 Babcock & Wilcox Co Steam generator
US2673553A (en) * 1950-03-01 1954-03-30 Babcock & Wilcox Co Multiple furnace fluid heating unit
US2637306A (en) * 1950-12-09 1953-05-05 Babcock & Wilcox Co Fluid cooled furnace
US2797668A (en) * 1952-09-29 1957-07-02 Babcock & Wilcox Co Fuel burning apparatus
US2827022A (en) * 1955-03-16 1958-03-18 Kohlenscheidungs Gmbh Radiant tubular boiler
US2897795A (en) * 1955-10-24 1959-08-04 Babcock & Wilcox Co Plural furnace single drum steam generating unit
US2921565A (en) * 1955-12-16 1960-01-19 Babcock & Wilcox Co Steam generating and superheating unit with downshot burners and gas recirculation temperature control
US2905157A (en) * 1956-04-23 1959-09-22 Combustion Eng Separately fired radiant superheater
US2952975A (en) * 1957-11-15 1960-09-20 Babcock & Wilcox Co Vapor generating and superheating unit
US2946187A (en) * 1958-05-28 1960-07-26 Foster Wheeler Corp Gas and steam cycle power plant having twin supercharged vapor generators
US3072109A (en) * 1958-05-28 1963-01-08 Foster Wheeler Corp Supercharged vapor generator
US3060907A (en) * 1961-07-27 1962-10-30 Riley Stoker Corp Steam generating unit
US3146759A (en) * 1962-03-19 1964-09-01 Riley Stoker Corp Steam generating unit
US3146760A (en) * 1962-07-16 1964-09-01 Riley Stoker Corp Steam generating unit
US3189006A (en) * 1962-11-20 1965-06-15 Combustion Eng Apparatus and method for starting a vapor generating power plant
US3265039A (en) * 1964-09-29 1966-08-09 Combustion Eng Burning chamber cells formed by horizontal partition-forming tubes
US3265038A (en) * 1964-09-29 1966-08-09 Combustion Eng Cellulosic fuel furnace having multi-cell burning chamber
CH532749A (de) * 1970-12-31 1973-01-15 Sulzer Ag Dampferzeuger
CH585876A5 (zh) * 1975-05-07 1977-03-15 Ofag Ofenbau Feuerungstech Ag
DE3113417A1 (de) * 1980-10-29 1982-09-02 Ruhrgas Ag, 4300 Essen Heizungsanlage mit einer absorptionswaermepumpe und verfahren zu deren betrieb
EP0075041B1 (de) * 1981-09-15 1986-03-05 GebràœDer Sulzer Aktiengesellschaft Dampferzeuger mit Überhitzerrohrwand
US4745884A (en) * 1987-05-28 1988-05-24 Riley Stoker Corporation Fluidized bed steam generating system
DE59301406D1 (de) * 1992-09-30 1996-02-22 Siemens Ag Verfahren zum Betreiben einer Kraftwerksanlage sowie danach arbeitende Anlage
DE19528438C2 (de) * 1995-08-02 1998-01-22 Siemens Ag Verfahren und System zum Anfahren eines Durchlaufdampferzeugers
JP3916784B2 (ja) * 1998-10-26 2007-05-23 バブコック日立株式会社 ボイラ構造
US6213059B1 (en) * 1999-01-13 2001-04-10 Abb Combustion Engineering Inc. Technique for cooling furnace walls in a multi-component working fluid power generation system
DE19901621A1 (de) * 1999-01-18 2000-07-27 Siemens Ag Fossilbeheizter Dampferzeuger
DE19914761C1 (de) * 1999-03-31 2000-09-28 Siemens Ag Fossilbeheizter Durchlaufdampferzeuger
DE19914760C1 (de) * 1999-03-31 2000-04-13 Siemens Ag Fossilbeheizter Durchlaufdampferzeuger
DE19929088C1 (de) * 1999-06-24 2000-08-24 Siemens Ag Fossilbeheizter Dampferzeuger mit einer Entstickungseinrichtung für Heizgas
EP1308671A1 (en) * 2001-10-30 2003-05-07 Alstom (Switzerland) Ltd A circulating fluidized bed reactor device
DE10254780B4 (de) * 2002-11-22 2005-08-18 Alstom Power Boiler Gmbh Durchlaufdampferzeuger mit zirkulierender atmosphärischer Wirbelschichtfeuerung
EP1701091A1 (de) * 2005-02-16 2006-09-13 Siemens Aktiengesellschaft Durchlaufdampferzeuger
EP1710498A1 (de) * 2005-04-05 2006-10-11 Siemens Aktiengesellschaft Dampferzeuger
US7587996B2 (en) * 2006-06-07 2009-09-15 Babcock & Wilcox Power Generation Group, Inc. Circulation system for sliding pressure steam generator
US8096268B2 (en) * 2007-10-01 2012-01-17 Riley Power Inc. Municipal solid waste fuel steam generator with waterwall furnace platens
EP2180250A1 (de) * 2008-09-09 2010-04-28 Siemens Aktiengesellschaft Durchlaufdampferzeuger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3288117A (en) * 1965-12-01 1966-11-29 Combustion Eng Arrangement of tube circuits in supercritical forced through-flow vapor generator
EP0308728A1 (de) * 1987-09-21 1989-03-29 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Durchlaufdampferzeugers
US5787844A (en) * 1995-03-06 1998-08-04 Ahlstrom Machinery Oy Economizer system
EP0884526A1 (en) * 1996-12-17 1998-12-16 Babcock-Hitachi Kabushiki Kaisha Boiler
DE19717158A1 (de) * 1997-04-23 1998-11-05 Siemens Ag Durchlaufdampferzeuger und Verfahren zum Anfahren eines Durchlaufdampferzeugers
EP1188986A2 (en) * 2000-09-18 2002-03-20 Kvaerner Pulping Oy Arrangement in recovery boiler

Also Published As

Publication number Publication date
JP5225469B2 (ja) 2013-07-03
EP2324286B1 (de) 2013-04-17
DK2324286T3 (da) 2013-05-13
CN102149968B (zh) 2014-04-30
PL2324286T3 (pl) 2013-09-30
AU2009290998A1 (en) 2010-03-18
JP2012502248A (ja) 2012-01-26
CN102149968A (zh) 2011-08-10
EP2324286A2 (de) 2011-05-25
WO2010028978A2 (de) 2010-03-18
WO2010028978A3 (de) 2010-06-17
AU2009290998B2 (en) 2014-03-20
US20110203536A1 (en) 2011-08-25

Similar Documents

Publication Publication Date Title
EP2321578B1 (de) Durchlaufdampferzeuger
EP1588095B1 (de) Dampferzeuger
EP2324286B1 (de) Durchlaufdampferzeuger
EP2324287B1 (de) Durchlaufdampferzeuger
WO1994027089A2 (de) Dampfkraftanlage zur erzeugung elektrischer energie
EP1848926A2 (de) Durchlaufdampferzeuger
EP2440847A2 (de) Durchlaufverdampfer
DE19914761C1 (de) Fossilbeheizter Durchlaufdampferzeuger
WO2015039831A2 (de) Gas-und-dampf-kombikraftwerk mit einem abhitzedampferzeuger
EP3014177B1 (de) Durchlaufdampferzeuger in zweizugkesselbauweise
DE102010038883C5 (de) Zwangdurchlaufdampferzeuger
DE102010038885B4 (de) Zwangdurchlaufdampferzeuger
DE4321619C2 (de) Verfahren zum Anfahren von Kraftwerksanlagen nach einem totalen Ausfall der Dampferzeugung
EP2364414B1 (de) Durchlaufdampferzeuger
WO2010102869A2 (de) Durchlaufverdampfer
EP2564117B1 (de) Dampferzeuger
WO2011138116A2 (de) Verfahren zum betreiben eines dampferzeugers
EP1533565A1 (de) Durchlaufdampferzeuger
DE102016111637A1 (de) Wasserrohrkesselanlage zur Erhitzung eines Mediums, Verfahren zur Erzeugung eines erhitzten Mediums und Verfahren zur Erzeugung elektrischer Energie

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

AKY No designation fees paid
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20101029

REG Reference to a national code

Ref country code: DE

Ref legal event code: R108

Effective date: 20110405

Ref country code: DE

Ref legal event code: 8566