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EP0778932B1 - Durchlaufdampferzeuger - Google Patents

Durchlaufdampferzeuger Download PDF

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Publication number
EP0778932B1
EP0778932B1 EP95928954A EP95928954A EP0778932B1 EP 0778932 B1 EP0778932 B1 EP 0778932B1 EP 95928954 A EP95928954 A EP 95928954A EP 95928954 A EP95928954 A EP 95928954A EP 0778932 B1 EP0778932 B1 EP 0778932B1
Authority
EP
European Patent Office
Prior art keywords
combustion chamber
evaporator tubes
steam generator
tube
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.)
Expired - Lifetime
Application number
EP95928954A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0778932A1 (de
Inventor
Joachim 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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Publication of EP0778932A1 publication Critical patent/EP0778932A1/de
Application granted granted Critical
Publication of EP0778932B1 publication Critical patent/EP0778932B1/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
    • 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
    • F22B29/061—Construction of tube walls
    • F22B29/062—Construction of tube walls involving vertically-disposed water tubes

Definitions

  • the invention relates to a once-through steam generator with a combustion chamber which is rectangular in cross section, each of which Combustion chamber wall arranged essentially vertically and over Pipe webs includes evaporator tubes connected to one another in a gas-tight manner, that of a flow medium from bottom to top are flowable.
  • the heating leads from the In contrast to combustion chamber walls forming evaporator tubes a natural circulation steam generator with only partial evaporation of the circulating water-water / steam mixture a complete evaporation of the flow medium in the Evaporator tubes in one pass. While with the natural circulation steam generator the evaporator tubes are basically vertical are arranged, the evaporator tubes of the continuous or forced-flow steam generator both vertically and helical - and thus inclined - be arranged.
  • a once-through steam generator whose combustion chamber walls are vertical arranged evaporator tubes is built is opposite one with a helical tube Continuous steam generator to produce more cost-effectively.
  • Continuous steam generator with vertical tubing also face those with inclined evaporator tubes lower water / steam side pressure losses. However, they can unavoidable differences in the heat input to the individual vertically arranged evaporator tubes to temperature differences between adjacent evaporator tubes - in particular at the outlet of the evaporator.
  • a compensation of the temperature curve in horizontal Direction - and thus a good heating compensation - is at the helical tube of the combustion chamber (spiral winding) achieved since each evaporator tube or parallel tube runs through practically all heating zones of the combustion chamber.
  • the spiral winding leads to one in comparison vertical tubing due to comparatively small entry areas of the evaporator tubes and thus one comparatively low total number of evaporator tubes at higher speeds of the flow medium in the evaporator tubes. This in turn leads to a comparatively high water / steam-side pressure loss.
  • the invention has for its object one for high Continuous steam generator designed for thermal efficiencies to be indicated with vertically piped combustion chamber walls in which the temperature differences at the evaporator outlet to particularly low values are reduced.
  • This object is achieved in that a from a single evaporator tube and the associated one Pipe web formed heat absorption surface in evaporator tubes in the central area of the combustion chamber wall is smaller than in a corner of the combustion chamber.
  • the invention is based on the consideration that the Heat absorption of the evaporator tubes not only via the gas side Half of the pipe circumference, but also over the pipe webs or tubular fins.
  • the self does not cooled pipe webs absorbed heat to the neighboring Evaporator tubes released.
  • the heat absorption area of an individual Evaporator tube is therefore composed of the Half of the flame body facing the inside of the combustion chamber.
  • the circumference of the evaporator tube and the area of a tube web The area of a pipe web results from the entire width of a pipe web or two times half the width of two Pipe webs and from its length in the vertical direction.
  • the width of the Pipe webs starting from the middle area to the corners of the Combustion chamber, successively to.
  • the evaporator tubes each combustion chamber wall into groups with tube webs each because the same width summarized, the width of the Pipe webs of different groups is different. This The alternative is practically simpler than the former perform.
  • the evaporator tubes in the area of the corners of the combustion chamber have additional tube webs in the combustion chamber protrude into it.
  • smooth tubes are expediently included a smooth inner surface.
  • the advantages achieved with the invention are in particular in that by reducing the heat absorption area in the middle of the combustion chamber walls in contrast to the Corners of the combustion chamber the different heat input into the individual evaporator tubes is equalized.
  • the width of the webs or fins between the evaporator tubes not - as before - over the entire circumference of the combustion chamber the same, but smaller in the middle of the wall than in the combustion chamber corners is selected, decreases in the The heat-absorbing surface for each individual in the middle of the wall Evaporator tube and it enlarges in the corners. Accordingly the heat absorption decreases or increases of the individual evaporator tubes. This causes the high heat input into one arranged in the middle of a combustion chamber wall Evaporator tube reduced and the lower heat input in an evaporator tube arranged in the corner of the combustion chamber wall will be raised.
  • a continuous steam generator 2 is shown schematically in FIG shown rectangular cross section, its vertical throttle cable is formed from a surrounding wall 4, which at the lower end passes into a funnel-shaped bottom 6.
  • the bottom 6 includes a discharge opening 8 not shown for Ash.
  • the throttle cable In the lower area A of the throttle cable are a number of burners 10 of which only one is visible to a fossil Fuel in the from vertically arranged evaporator tubes 12 formed surrounding wall or combustion chamber 4 attached.
  • the vertically arranged evaporator tubes 12 are in this area A over tube fins or tube webs 14 (figures 2 and 3) in the form of metal strips for gas-tight combustion chamber walls 4a welded together.
  • the operation of the Flow-through steam generator 2 flowed from bottom to top Evaporator tubes 12 form an evaporator heating surface in this area A. 16.
  • the combustion steam generator 4 is located in the combustion chamber 4 during operation 2 one when burning the fossil Fuel arising flame body 17, so that this Area A of the continuous steam generator 2 by a very high Excellent heat flow density.
  • the flame body 17 has a Temperature profile on that, starting from about the middle of the Combustion chamber 4, both in the vertical direction and up down as well as horizontally to the sides, that is, decreases towards the corners of the combustion chamber 4.
  • A is located above the lower area A of the throttle cable second flame distant area B, above which a third upper one Area C of the throttle cable is provided. In areas B and C of the throttle cable, convection heating surfaces 18, 20 and 22 are arranged. A is located above area C of the throttle cable Flue gas outlet channel 24, through which the combustion of the fossil fuel flue gas RG the vertical Throttle cable leaves.
  • FIGS. 2 and 3 each show a cross section in the detail through the combustion chamber 4 in area A of the gas flue, whereby two combustion chamber walls adjoining a corner 26, 26 ' 4a ( Figure 2) and 4a '( Figure 3) are shown.
  • 4a ' are those between neighboring ones Evaporator tubes 12, 12 'provided tube webs 14 or 14 'welded to these on the longitudinal side. This design is also referred to as tube-web-tube construction.
  • each combustion chamber wall 4a, 4a ' is constructed from approximately 360 evaporator tubes 12 and 12', respectively.
  • d 1 , d '/ 1 of the evaporator tubes 12, 12' of approximately 30 mm and a width b, b 'of the tube webs 14, 14' of approximately 20 mm
  • the overall width of each combustion chamber wall 4a or 4a ' is approximately 20 m.
  • the heat absorption surface F' results also from each half the width b 'of two to the evaporator tube 12 'adjacent pipe webs 14' and again the half the circumference of the individual evaporator tube 12 'and its Length.
  • This latter definition is based on the consideration that on the one hand the temperature of each tube web 14, 14 ' on its half width b, b ', that is in the middle of the Rohrstegs 14, 14 ', has the highest value and to the two adjacent evaporator tubes 12 or 12 'decreases. To the others give each pipe web 14, 14 'its heat Half to the two adjacent evaporator tubes 12 and 12 ' from.
  • the width b the tube webs 14 between the evaporator tubes 12 from the Center of each combustion chamber wall 4a to each corner 26 of the combustion chamber 4 gradually, that is gradually, to.
  • heat absorption surface F of the individual evaporator tubes 12 from each corner 26 of the combustion chamber 4 every combustion chamber wall 4a to the Middle is reduced.
  • the fin width b thus decreases same heat supply per area the heat absorption per evaporator tube 12.
  • a resulting lower heat flow density leads to the outside of the evaporator tube 12 a reduced amount of heat on the inside of the evaporator tube 12. This goes both the local heat flow density as well as over the total height of the once-through steam generator 2 the integral heat flow density. this leads to good local cooling of the evaporator tubes 12.
  • each combustion chamber wall 4a' to groups G1 to G4 combined with tube webs 14 'each of the same width b'.
  • the width b 'of the tube webs 14' is different Groups G1, G2, G3 and G4 different.
  • the width b 'of Pipe webs 14 'of those groups that the corner 26' of Adjacent combustion chamber 4 is preferably the same. In the embodiment these are the tube webs 14 'of group G1 and a group G5 of the two adjacent to the corner 26 ' Combustion chamber walls 4a '.
  • Evaporator tubes 12 and 12 ' are smooth tubes with a smooth surface on the inside.
  • 4a 'of the continuous steam generator 2 with such internally ribbed Evaporator tubes 12 and 12 'of the axial flow in a swirl is superimposed on the evaporator tubes 12, 12 ', so that due to an additional speed component a particularly good cooling effect of the evaporator tubes 12, 12 'is achieved.
  • This has a particularly advantageous effect in the operation of the continuous steam generator 2 in the critical Pressure range at about 210 bar.

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)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Gas Burners (AREA)
EP95928954A 1994-09-01 1995-08-21 Durchlaufdampferzeuger Expired - Lifetime EP0778932B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4431185 1994-09-01
DE4431185A DE4431185A1 (de) 1994-09-01 1994-09-01 Durchlaufdampferzeuger
PCT/DE1995/001103 WO1996007053A1 (de) 1994-09-01 1995-08-21 Durchlaufdampferzeuger

Publications (2)

Publication Number Publication Date
EP0778932A1 EP0778932A1 (de) 1997-06-18
EP0778932B1 true EP0778932B1 (de) 1998-07-22

Family

ID=6527192

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95928954A Expired - Lifetime EP0778932B1 (de) 1994-09-01 1995-08-21 Durchlaufdampferzeuger

Country Status (8)

Country Link
US (1) US5979370A (es)
EP (1) EP0778932B1 (es)
JP (1) JP3046890U (es)
KR (1) KR100368516B1 (es)
CN (1) CN1107202C (es)
DE (2) DE4431185A1 (es)
ES (1) ES2119461T3 (es)
WO (1) WO1996007053A1 (es)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2208739C2 (ru) * 1998-06-10 2003-07-20 Сименс Акциенгезелльшафт Прямоточный парогенератор, работающий на ископаемом топливе
DE19825800A1 (de) * 1998-06-10 1999-12-16 Siemens Ag Fossilbeheizter Dampferzeuger
DE19858780C2 (de) 1998-12-18 2001-07-05 Siemens Ag Fossilbeheizter Durchlaufdampferzeuger
DE19901621A1 (de) 1999-01-18 2000-07-27 Siemens Ag Fossilbeheizter Dampferzeuger
DE19901430C2 (de) 1999-01-18 2002-10-10 Siemens Ag Fossilbeheizter Dampferzeuger
DE10254780B4 (de) * 2002-11-22 2005-08-18 Alstom Power Boiler Gmbh Durchlaufdampferzeuger mit zirkulierender atmosphärischer Wirbelschichtfeuerung
EP1512907A1 (de) * 2003-09-03 2005-03-09 Siemens Aktiengesellschaft Verfahren zum Anfahren eines Durchlaufdampferzeugers und Durchlaufdampferzeuger zur Durchführung des Verfahrens
EP1533565A1 (de) * 2003-11-19 2005-05-25 Siemens Aktiengesellschaft Durchlaufdampferzeuger
DE102005060704A1 (de) * 2005-12-19 2007-06-28 Rolls-Royce Deutschland Ltd & Co Kg Gasturbinenbrennkammer
TW200946838A (en) * 2008-03-04 2009-11-16 Ihi Corp Heating apparatus
EP2182278A1 (de) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Durchlaufdampferzeuger
EP2180250A1 (de) * 2008-09-09 2010-04-28 Siemens Aktiengesellschaft Durchlaufdampferzeuger
CN101725955B (zh) * 2008-10-16 2012-04-04 林光湧 环保常压高温蒸汽发生器
US20100281864A1 (en) * 2009-05-06 2010-11-11 General Electric Company Organic rankine cycle system and method
GB201010038D0 (en) 2010-06-16 2010-07-21 Doosan Power Systems Ltd Steam generator
DE102013215456A1 (de) 2013-08-06 2015-02-12 Siemens Aktiengesellschaft Durchlaufdampferzeuger

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE429171C (de) * 1923-06-01 1926-05-21 Thomas Edward Murray Dampfkessel mit die Verbrennungskammer umgebenden Waenden aus in Abstaenden nebeneinander angeordneten Rohren
US1854342A (en) * 1925-01-20 1932-04-19 Combustion Eng Corp Art of combustion and steam generation
NL129291C (es) * 1961-07-27
US3375628A (en) * 1965-07-01 1968-04-02 Foster Whceler Corp Insulated wall construction for heated surfaces
US3301224A (en) * 1965-12-13 1967-01-31 Combustion Eng Steam generator organization
JPS5623603A (en) * 1979-08-01 1981-03-06 Mitsubishi Heavy Ind Ltd Forced flowinggthrough boiler
DE58905817D1 (de) * 1988-07-26 1993-11-11 Siemens Ag Durchlaufdampferzeuger.
DK0503116T4 (da) * 1991-03-13 1998-08-31 Siemens Ag Rør med ribber, som på dets inderside danner et flergænget gevind, samt dampgenerator til dets anvendelse
ATE117420T1 (de) * 1991-04-18 1995-02-15 Siemens Ag Durchlaufdampferzeuger mit einem vertikalen gaszug aus im wesentlichen vertikal angeordneten rohren.
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
DE59502913D1 (de) 1998-08-27
KR100368516B1 (ko) 2003-03-15
DE4431185A1 (de) 1996-03-07
CN1107202C (zh) 2003-04-30
CN1155326A (zh) 1997-07-23
EP0778932A1 (de) 1997-06-18
JP3046890U (ja) 1998-03-24
ES2119461T3 (es) 1998-10-01
KR970705724A (ko) 1997-10-09
WO1996007053A1 (de) 1996-03-07
US5979370A (en) 1999-11-09

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