EP0657010B2 - Dampferzeuger - Google Patents

Dampferzeuger Download PDF

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Publication number
EP0657010B2
EP0657010B2 EP93917528A EP93917528A EP0657010B2 EP 0657010 B2 EP0657010 B2 EP 0657010B2 EP 93917528 A EP93917528 A EP 93917528A EP 93917528 A EP93917528 A EP 93917528A EP 0657010 B2 EP0657010 B2 EP 0657010B2
Authority
EP
European Patent Office
Prior art keywords
tubes
steam generator
gas flue
section
generator according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93917528A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0657010B1 (de
EP0657010A1 (de
Inventor
Wolfgang Köhler
Rudolf Kral
Eberhard Wittchow
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=6465884&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0657010(B2) "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 EP0657010A1 publication Critical patent/EP0657010A1/de
Application granted granted Critical
Publication of EP0657010B1 publication Critical patent/EP0657010B1/de
Publication of EP0657010B2 publication Critical patent/EP0657010B2/de
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
    • 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
    • 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
    • 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
    • F22B37/14—Supply mains, e.g. rising mains, down-comers, in connection with water tubes

Definitions

  • the invention relates to a fossil-fired once-through steam generator with a throttle cable, the surrounding wall of interconnected gas-tight tubes is formed, which in arranged essentially vertically and parallel on the medium side can flow from bottom to top.
  • the surrounding wall is often from heating surface element to heating surface element exposed to different levels of heating. So is usually in the lower part, in which a number of Burners for the fossil fuel are arranged, the heating much stronger than in the upper part. The reason this is also due to the fact that in this upper part often additional heat exchanger surfaces are arranged, which the Surrounding wall against excessive heating, in particular shield by heat radiation.
  • the invention is therefore based on the object Steam generator of the type mentioned above to further develop that, on the one hand, adequate cooling the pipes of the surrounding wall are ensured, and that, on the other hand, more individual heating Pipes not too impermissible temperature differences leads between the individual pipes. This is said to be with little Costs can be achieved.
  • this object is achieved by that the pipes in a downstairs first Part of the throttle cable has a larger inner diameter have than the pipes in an overlying second part of the throttle cable.
  • the first part of the throttle cable below which is in the following as the first section of the perimeter wall is characterized by very high Heat flow densities and good internal heat transfer in the pipes and lies e.g. in the burner area.
  • the second part of the throttle cable in the following also as a second section of the surrounding wall is also noted due to high heat flow densities, but a worsened one internal heat transfer in the pipes and lies e.g. in the so-called gas jet room of the steam generator, which is located at the burner area connects.
  • the first section of the surrounding wall expediently comprises internally finned, vertically arranged tubes to improve the internal heat transfer. These are preferably dimensioned such that the average mass flow density in the tubes at full load is preferably less than 1000 kg / m 2 s.
  • the steam has an average steam content at the outlet of the first section, which is between 0.8 and 0.95 at a partial load of about 40%. Under these conditions, the flow conditions are so favorable that additional heating of individual tubes leads to increased throughput through these tubes, so that only small temperature differences occur at the outlet of the tubes.
  • the mass flow density is preferably increased to more than 1000 kg / m 2 s. Therefore, the inside diameter of the pipes at the transition from the first to the second section is reduced while maintaining the same number of parallel pipes or pipe divisions. By reducing the inside diameter, safe pipe cooling is guaranteed even with a high heat flow density in the second section.
  • the tubes with the smaller inside diameter of the second section are advantageously directly to the Larger inner diameter tubes of the first section connected so that the pipes of the two Merge sections directly into one another.
  • the pipes of the second section can flow at least in the first Part also have internal ribbing.
  • a pressure compensation pipe is connected to each pipe.
  • the pressure compensation tubes are expedient to one or more outside the vertical Accelerator cable provided pressure compensation tanks guided.
  • a steam generator with a high throttle cable e.g. a draw-in type steam generator
  • This third part of the throttle cable which is also referred to as the third Section of the surrounding wall is drawn is characterized by a low heat flow density and a moderate internal heat transfer in the pipes and lies in the so-called convection train of the Steam generator.
  • the surrounding wall reduces the mass flow density the low heat flux density prevailing there opposite to that in the second section to keep the friction pressure loss in the pipes low.
  • the pipes can be made without internal fins be trained.
  • the vertical throttle cable of the steam generator 1 according to Figure 1 with a rectangular cross-section is through a Surrounding wall 2 formed at the lower end of the Throttle cable passes into a funnel-shaped base 3.
  • the tubes 4 of the surrounding wall 2 are on their Long sides - e.g. over fins 9 ( Figure 2) - gastight interconnected, e.g. welded.
  • the floor 3 includes a discharge opening, not shown 3a for ashes.
  • a lower or first part 5 of the throttle cable i.e. in a first section of the surrounding wall 2
  • tubes 4 the surrounding wall 2 curved; they run on the Outside of the vertical throttle cable. Similar openings can also e.g. for air nozzles or flue gas nozzles be educated.
  • a second part 7 of the throttle cable i.e. a second Section of the surrounding wall 2 over which a third or upper part 8 of the throttle cable, i.e. a third section the surrounding wall 2 is provided.
  • the first section 5 draws in the burner area is characterized by a very high heat flow density and a good internal heat transfer in the tubes 4.
  • the second section 7 is located in the gas jet chamber and is also characterized by a high heat flow density, but also by a smaller, worse one internal heat transfer in the pipes 4 out.
  • the third section 8 is located in the convection train and is characterized by a low heat flow density and a moderate internal heat transfer in the tubes 4. This third section 8 is especially with a steam generator in a pull-in construction available.
  • the medium side, i.e. of water or one Water-steam mixture, parallel from bottom to top flowed through tubes 4 of the surrounding wall 2 are with their entry ends to an entry collector 11 and with their outlet ends to an outlet collector 12 connected.
  • the entry collector 11 and the exit collector 12 are outside the throttle cable and are e.g. each formed by an annular tube.
  • the inlet header 11 is via a line 13 and a collector 14 with the output of a high pressure preheater or economizers 15 connected.
  • the heating surface the economizer 15 is in the third section 8 of the surrounding wall 2 included space.
  • Of the Economizer 15 is during the operation of the steam generator 1 on the input side via a collector 16 connected to the water-steam cycle of a steam turbine.
  • the outlet header 12 is via a water-steam separation vessel 17 and a line 18 with a High pressure superheater 19 connected.
  • the high pressure superheater 19 is in the area of the second section 7 the surrounding wall 2 arranged. He is during the Operation on the output side via a collector 20 with a High pressure part of the steam turbine connected.
  • a collector 20 with a High pressure part of the steam turbine connected.
  • the collector 22, 23 between the high pressure part and a medium pressure part of the steam turbine is switched.
  • water-steam separation vessel 17 water is discharged via a line 24.
  • a pressure compensation vessel outside the throttle cable 26 provided, which is formed by an annular tube is.
  • each is in the sections 5 and 7 extending pipe 4 via a pressure compensation pipe 27 with the pressure compensation vessel 26 connected.
  • the inside width of the tubes 4 tapers.
  • the tubes 4 have a larger inner diameter d 1 in the lower part 5 of the throttle cable the pipes 4 in the overlying second part 7 of the throttle cable, the inside diameter of which is denoted by d 2 .
  • the tubes 4 with the smaller inner diameter d 2 are directly connected to the tubes 4 with the larger inner diameter d 1 , ie the tubes 4 merge into one another in the region 25.
  • the tubes 4 in section 5 have a thread-like internal ribbing in a manner not shown.
  • the tubes 4 are dimensioned in section 5 such that the mean mass flow density there is less than or equal to 1000 kg / m 2 s at full load. The average mass flow density in the tubes 4 is then greater than 1000 kg / m 2 s in the second or middle section 7.
  • the tubes 4 again have a larger inner diameter on than in the section below 7. While the tubes 4 also in the second section 7 preferably one over its entire length have thread-shaped inner ribs, are Pipes 4 of the third section 8 only over part of it Provide length with a thread-like internal ribbing. However, it is expedient to use internal ribbing waived.
  • the number of tubes 4 in the upper section 8 of the Boundary wall 2 is only half the size of the second Section 7. Therefore, two pipes 4 of the second open Section 7 in an area 30 in a common to them assigned tube 4 of the third section 8 (FIG 1).
  • the outer diameter of the tubes 4 in sections 5 and 7 is different and adapted to the respective inner diameter d 1 , d 2 such that the wall thickness of the tubes 4 is approximately the same in all sections 5, 7, 8 is. But it can also be the outer diameter of the tubes 4 in all sections 5, 7, 8 of the same size, so that the wall thickness of the tubes 4 in the middle or second section 7 is greater than in the first section 5 and / or in the third section 8.
  • the tubes 4 are provided on their long sides with fins 9 which are used for the gas-tight connection of the tubes 4.
  • the tubes 4 of the surrounding wall 2 along its length in different sections 5, 7, 8 or regions of the steam generator 1 has a different inner diameter d 1, d have 2, the dimensioning of the tubes 4 of the surrounding wall 2 on a different heating of the gas flue Voted.
  • reliable cooling of the tubes 4 is ensured.
  • additional heating of individual tubes 4 does not lead to impermissible temperature differences between the outputs of the individual tubes 4.

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)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Detergent Compositions (AREA)
  • Hydrogen, Water And Hydrids (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • Devices For Medical Bathing And Washing (AREA)
EP93917528A 1992-08-19 1993-08-06 Dampferzeuger Expired - Lifetime EP0657010B2 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4227457 1992-08-19
DE4227457A DE4227457A1 (de) 1992-08-19 1992-08-19 Dampferzeuger
PCT/DE1993/000698 WO1994004870A1 (de) 1992-08-19 1993-08-06 Dampferzeuger

Publications (3)

Publication Number Publication Date
EP0657010A1 EP0657010A1 (de) 1995-06-14
EP0657010B1 EP0657010B1 (de) 1996-12-04
EP0657010B2 true EP0657010B2 (de) 1999-08-25

Family

ID=6465884

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93917528A Expired - Lifetime EP0657010B2 (de) 1992-08-19 1993-08-06 Dampferzeuger

Country Status (17)

Country Link
US (1) US5701850A (ru)
EP (1) EP0657010B2 (ru)
JP (1) JP3188270B2 (ru)
KR (1) KR100209115B1 (ru)
CN (1) CN1043680C (ru)
AT (1) ATE145980T1 (ru)
CA (1) CA2142840A1 (ru)
CZ (1) CZ287735B6 (ru)
DE (2) DE4227457A1 (ru)
DK (1) DK0657010T4 (ru)
ES (1) ES2095660T5 (ru)
GR (1) GR3022186T3 (ru)
RU (1) RU2109209C1 (ru)
SK (1) SK22295A3 (ru)
TW (1) TW228565B (ru)
UA (1) UA27923C2 (ru)
WO (1) WO1994004870A1 (ru)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4426692C1 (de) * 1994-07-28 1995-09-14 Daimler Benz Ag Zweistufige Verdampfereinheit für einen Reaktant-Massenstrom und Verfahren zur Herstellung desselben
DE19548806C2 (de) * 1995-02-14 1998-03-26 Evt Energie & Verfahrenstech Verfahren und Anlage zur Erzeugung von Dampf mit überkritischen Dampfparameter in einem Durchlaufdampferzeuger
US5901669A (en) * 1995-04-05 1999-05-11 The Babcock & Wilcox Company Variable pressure once-through steam generator upper furnace having non-split flow circuitry
DE19644763A1 (de) * 1996-10-28 1998-04-30 Siemens Ag Dampferzeugerrohr
DE19651678A1 (de) * 1996-12-12 1998-06-25 Siemens Ag Dampferzeuger
US6092490A (en) * 1998-04-03 2000-07-25 Combustion Engineering, Inc. Heat recovery steam generator
CA2334699C (en) 1998-06-10 2008-11-18 Siemens Aktiengesellschaft Fossil-fuel-fired steam generator
DE19825800A1 (de) * 1998-06-10 1999-12-16 Siemens Ag Fossilbeheizter Dampferzeuger
IL134035A0 (en) * 2000-01-13 2001-04-30 Ronen Daniel A device, system and method for remote push-publishing of content onto display screens of mobile devices including a screen saver application
US6619041B2 (en) * 2001-06-29 2003-09-16 L'air Liquide - Societe Anonyme A Directoire Et Conseil De Surveillance Pour L'etude Et L'exploitation Des Procedes Georges Claude Steam generation apparatus and methods
EP1533565A1 (de) * 2003-11-19 2005-05-25 Siemens Aktiengesellschaft Durchlaufdampferzeuger
JP4787284B2 (ja) * 2007-03-27 2011-10-05 ダイキン工業株式会社 ヒートポンプ式給湯装置
US7594401B1 (en) * 2008-04-10 2009-09-29 General Electric Company Combustor seal having multiple cooling fluid pathways
JP5193007B2 (ja) * 2008-12-03 2013-05-08 三菱重工業株式会社 ボイラ構造
DE102009040250B4 (de) * 2009-09-04 2015-05-21 Alstom Technology Ltd. Zwangdurchlaufdampferzeuger für den Einsatz von Dampftemperaturen von über 650 Grad C
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
DE102010061186B4 (de) 2010-12-13 2014-07-03 Alstom Technology Ltd. Zwangdurchlaufdampferzeuger mit Wandheizfläche und Verfahren zu dessen Betrieb
JP2012220043A (ja) * 2011-04-04 2012-11-12 Mitsubishi Heavy Ind Ltd 蒸気発生器
CN102798114B (zh) * 2012-08-30 2014-09-03 上海锅炉厂有限公司 一种非均匀管径内螺纹管垂直管屏水冷壁布置方法

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US475479A (en) * 1892-05-24 Low-pressure steam-boiler
DE739376C (de) * 1940-01-17 1943-09-23 Rheinmetall Borsig Ag Wasserrohrdampferzeuger
GB574810A (en) * 1942-06-23 1946-01-22 Bbc Brown Boveri & Cie Heat exchanger for heating gases and vapours to a high temperature
US3221713A (en) * 1963-08-20 1965-12-07 Babcock & Wilcox Co Forced flow vapor generator
US3556059A (en) * 1969-01-28 1971-01-19 Foster Wheeler Corp Two-pass furnace circuit arrangement for once-through vapor generator
DE2557427A1 (de) * 1975-12-19 1977-06-30 Kraftwerk Union Ag Schaltung einer feuerraumnase bei einem durchlaufkessel mit gasdicht verschweissten waenden in zweizugbauweise
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
US4178881A (en) * 1977-12-16 1979-12-18 Foster Wheeler Energy Corporation Vapor generating system utilizing angularly arranged bifurcated furnace boundary wall fluid flow tubes
PL204072A1 (pl) * 1978-01-17 1979-09-24 Katowice Metalurgiczny Huta Kociol odzysknicowy,zwlaszcza dla konwertora stalowniczego
DE58905817D1 (de) * 1988-07-26 1993-11-11 Siemens Ag Durchlaufdampferzeuger.
DE4232880A1 (de) * 1992-09-30 1994-03-31 Siemens Ag Dampferzeuger
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

Also Published As

Publication number Publication date
US5701850A (en) 1997-12-30
TW228565B (ru) 1994-08-21
WO1994004870A1 (de) 1994-03-03
GR3022186T3 (en) 1997-03-31
UA27923C2 (ru) 2000-10-16
CN1083573A (zh) 1994-03-09
RU95106598A (ru) 1996-12-27
CN1043680C (zh) 1999-06-16
DE4227457A1 (de) 1994-02-24
KR100209115B1 (ko) 1999-07-15
CZ37595A3 (en) 1995-08-16
DK0657010T4 (da) 1999-12-13
CZ287735B6 (en) 2001-01-17
ES2095660T5 (es) 1999-11-16
ATE145980T1 (de) 1996-12-15
ES2095660T3 (es) 1997-02-16
CA2142840A1 (en) 1994-03-03
KR950703135A (ko) 1995-08-23
JP3188270B2 (ja) 2001-07-16
SK22295A3 (en) 1995-07-11
RU2109209C1 (ru) 1998-04-20
EP0657010B1 (de) 1996-12-04
DK0657010T3 (da) 1997-06-02
EP0657010A1 (de) 1995-06-14
JPH08500426A (ja) 1996-01-16
DE59304695D1 (de) 1997-01-16

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