EP0778932A1 - Generateur continu de vapeur - Google Patents

Generateur continu de vapeur

Info

Publication number
EP0778932A1
EP0778932A1 EP95928954A EP95928954A EP0778932A1 EP 0778932 A1 EP0778932 A1 EP 0778932A1 EP 95928954 A EP95928954 A EP 95928954A EP 95928954 A EP95928954 A EP 95928954A EP 0778932 A1 EP0778932 A1 EP 0778932A1
Authority
EP
European Patent Office
Prior art keywords
combustion chamber
tube
evaporator
steam generator
evaporator tubes
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
EP95928954A
Other languages
German (de)
English (en)
Other versions
EP0778932B1 (fr
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
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
Publication of EP0778932A1 publication Critical patent/EP0778932A1/fr
Application granted granted Critical
Publication of EP0778932B1 publication Critical patent/EP0778932B1/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
    • 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 combustion chamber of which comprises and essentially vertically arranged and gas-tightly connected evaporator tubes, through which a flow medium can flow from bottom to top.
  • the heating of the evaporator tubes forming the combustion chamber walls in contrast to a natural circulation steam generator with only partial evaporation of the water-water / steam mixture circulating, leads to complete evaporation of the flow medium in the evaporator tubes in one pass.
  • the evaporator tubes While in the natural circulation steam generator the evaporator tubes are in principle arranged vertically, the evaporator tubes of the once-through or forced-flow steam generator can be arranged both vertically and helically - and thus inclined.
  • a continuous steam generator the combustion chamber walls of which is constructed from vertically arranged evaporator tubes, is compared to one with a helical tube
  • Continuous steam generator to produce more cost-effectively.
  • Continuous-flow steam generators with vertical pipes also have lower water / steam-side pressure losses than those with inclined evaporator tubes.
  • the unavoidable differences in the heat supply to the individual vertically arranged evaporator tubes can lead to temperature differences between adjacent evaporator tubes - especially at the outlet of the evaporator.
  • the continuous-flow steam generator with vertically tube-shaped combustion chamber walls is usually operated with relatively high mass flow densities in the evaporator tubes in order to always have a sufficiently high heat transfer from the evaporator tube wall to the flow or heat absorption medium in the critical pressure range from about 200 bar to 221 bar to reach.
  • these measures primarily take into account the temperature profile in the vertical direction of the combustion chamber.
  • a compensation of the temperature curve in the horizontal direction - and thus a good heating compensation - is achieved with the helical tubing of the combustion chamber (spiral winding), since each evaporator tube or parallel tube runs through practically all heating zones of the combustion chamber.
  • the spiral winding leads to higher velocities of the flow medium in the evaporator tubes in comparison to vertical tubing due to the comparatively small inlet areas of the evaporator tubes and thus a comparatively small total number of evaporator tubes. This in turn leads to a comparatively high pressure drop on the water / steam side.
  • the invention is based on the object of specifying a continuous steam generator designed for high thermal efficiencies with vertically tubular combustion chamber walls, in which the temperature differences at the evaporator outlet are reduced to particularly low values.
  • This object is achieved according to the invention in that a heat-absorbing surface formed from a single evaporator tube and the tube web assigned to it is provided in the case of evaporator tubes. ren 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 takes place not only via the gas-side half of the tube circumference, but also via the tube webs or tube fins.
  • the heat absorbed by the non-cooled tube webs is given off to the neighboring evaporator tubes.
  • the heat absorption surface of an individual evaporator tube is therefore composed of the half circumference of the evaporator tube facing the flame body in the interior of the combustion chamber and the surface of a tube web.
  • the area of a tube web results from the entire width of a tube web or from twice the width of two tube webs and from its length in the vertical direction.
  • the width of the connecting the evaporator tubes is expedient
  • Pipe webs in the middle area of each combustion chamber wall are smaller than in the corners of the combustion chamber.
  • the width of the tube webs starting from the central area to the corners of the tube
  • combustion chamber walls with vertically arranged evaporator tubes and with tube webs of different widths can also expediently be simplified in that the width of the tube webs of groups adjacent to the corners of each wall of the combustion chamber is the same.
  • the evaporator tubes can have additional tube webs in the area of the corners of the combustion chamber, which protrude into the combustion chamber.
  • smooth pipes with a smooth inner surface are expediently used.
  • internally finned pipes can also be used.
  • a variation of the tube inner and / or the tube outer diameter can additionally even out the different heat supply in a single evaporator tube.
  • an evaporator tube with a larger diameter than an evaporator tube in the middle of a combustion chamber wall is then inserted.
  • the advantages achieved by the invention are, in particular, that by reducing the heat absorption area in the central region of the combustion chamber walls, in contrast to the corners of the combustion chamber, the different heat supply into the individual evaporator tubes is made more uniform. Because the width of the tube webs or tube fins between the evaporator tubes is not chosen to be the same over the entire circumference of the combustion chamber as before, but rather is smaller in the wall centers than in the corners of the combustion chamber, the heat-absorbing area for each individual is reduced in the wall centers Evaporator tube and it enlarges in the corners. Accordingly, the heat absorption of the individual evaporator tubes is reduced or increased.
  • FIG. 1 shows a simplified representation of a continuous steam generator with vertically arranged evaporator tubes
  • FIG. 2 shows a detail of a cross section along the line II-II in FIG. 1 with gas-tight combustion chamber walls with pipe webs of different widths
  • FIG. 3 shows a section according to FIG. 2 with groups of evaporator tubes with web widths that are the same in groups.
  • a continuous steam generator 2 is shown schematically with a rectangular cross section, the vertical gas train is formed from a surrounding wall 4, which merges into a funnel-shaped bottom 6 at the lower end.
  • the bottom 6 comprises a discharge opening 8 for ashes, not shown.
  • a number of burners 10, only one of which is visible, are attached for a fossil fuel in the peripheral wall or combustion chamber 4 formed from vertically arranged evaporator tubes 12.
  • the vertically arranged evaporator tubes 12 are welded together in this area A via tube fins or tube webs 14 (FIGS. 2 and 3) in the form of metal strips to form gas-tight combustion chamber walls 4a.
  • the evaporator tubes 12 flowed through from bottom to top during operation of the continuous steam generator 2 form an evaporator heating surface 16 in this area A.
  • the continuous steam generator 2 when the continuous steam generator 2 is operating, there is a combustion of the fossil fuel Fuel resulting flame body 17, so that this area A of the continuous steam generator 2 is characterized by a very high heat flow density.
  • the flame body 17 has a temperature profile which, starting from approximately the center of the combustion chamber 4, decreases both in the vertical direction upwards and downwards and in the horizontal direction to the sides, that is to say to the corners of the combustion chamber 4.
  • FIGS. 2 and 3 each show a cross section through the combustion chamber 4 in area A of the throttle cable, two combustion chamber walls adjoining a corner 26, 26 '
  • each combustion chamber wall 4a, 4a ' is made up of approximately 360 evaporator tubes 12 or 12 '.
  • d ] _ With an outer diameter d ] _, d ⁇ 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, a total width of each results Combustion chamber wall 4a or 4a 'of approximately 20 m.
  • the heat absorption surface F of the respective evaporator tube 12 results from the width b of the tube webs 14 and the half circumference 12a of the evaporator tube 12 and its length. This is illustrated in FIG. 2 on a single evaporator tube 12.
  • the heat absorption surface F' also results from half the width b 'of two tube webs 14' adjoining the evaporator tube 12 'and again 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 'at its half width b, b', that is to say in the middle of the tube web 14, 14 ', has the highest value and the two adjacent evaporator tubes 12 or 12 'decreases.
  • each tube web 14, 14 ' gives half of its heat to the two adjacent evaporator tubes 12 and 12', respectively.
  • the width b of the tube webs 14 between the evaporator tubes 12 gradually, that is to say gradually, decreases from the center of each combustion chamber wall 4a to each corner 26 of the combustion chamber 4. If the length of the evaporator tube 12 and the tube webs 14 is the same, the heat absorption area F of the individual evaporator tubes 12 is continuously reduced from the center of each combustion chamber wall 4a to each corner 26 of the combustion chamber 4. The fin width b is thus reduced with the same heat supply per surface, the heat absorption per evaporator tube 12. A resulting lower heat flow density on the outside of the evaporator tube 12 leads to a reduced amount of heat on the inside of the evaporator tube 12.
  • the evaporator tubes 12 'of each combustion chamber wall 4a' are combined into groups G1 to G4 with tube webs 14 'each having the same width b'.
  • the width b 'of the tube webs 14' of different G 'groups Gl, G2, G3 and G4 different.
  • the width b 'of the tube webs 14' of those groups, the adjacent 4-lock chamber to the corner 26 'of B is preferably the same.
  • these are the tube webs 14 'of the group G1 and a group G5 of the two combustion chamber walls 4a' adjacent to the corner 26 '.
  • the evaporator tubes 12 'of the combustion chamber 4 arranged in the area of the corner 26' have additional tube webs 14 '' which protrude into the combustion chamber 4 with different inclinations.
  • the evaporator tubes 12 and 12 'shown in the exemplary embodiments according to FIGS. 2 and 3 are smooth tubes with a smooth surface on the inside.

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)
  • Gas Burners (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

L'invention concerne un générateur continu de vapeur comprenant une chambre de combustion (4) de section rectangulaire dont chaque paroi (4a, 4a') est disposée sensiblement verticalement et comprend des tubes évaporatoires (12, 12') reliés les uns aux autres de manière étanche aux gaz, par l'intermédiaire d'entretoises tubulaires (14, 14') et traversés par une substance qui s'écoule de bas en haut. Afin de compenser une adduction différente de chaleur dans les tubes évaporatoires (12, 12'), il est prévu qu'une surface d'absorption thermique (F, F') composée d'un seul tube évaporatoire (12, 12') et d'une entretoise tubulaire (14, 14') qui lui est associée, surface située au niveau de tubes évaporatoires (12, 12') se trouvant dans la zone médiane de la paroi (4a, 4a') de la chambre de combustion, soit plus petite que dans un coin (26, 26') de la chambre de combustion (4).
EP95928954A 1994-09-01 1995-08-21 Generateur continu de vapeur Expired - Lifetime EP0778932B1 (fr)

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 (fr) 1994-09-01 1995-08-21 Generateur continu de vapeur

Publications (2)

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

Family

ID=6527192

Family Applications (1)

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

Country Status (8)

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

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19825800A1 (de) * 1998-06-10 1999-12-16 Siemens Ag Fossilbeheizter Dampferzeuger
DK1086339T3 (da) 1998-06-10 2002-04-15 Siemens Ag Fossilt fyret gennemløbsdampgenerator
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 (fr) * 2003-09-03 2005-03-09 Siemens Aktiengesellschaft Procédé pour le demarrage d'un générateur de vapeur à passage unique et le générateur de vapeur à passage unique pour la mise en oeuvre du procédé
EP1533565A1 (fr) * 2003-11-19 2005-05-25 Siemens Aktiengesellschaft Générateur de vapeur à passage unique
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
EP2180250A1 (fr) * 2008-09-09 2010-04-28 Siemens Aktiengesellschaft Générateur de vapeur en continu
EP2182278A1 (fr) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Générateur de vapeur en continu
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
BE620763A (fr) * 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
EP0352488B1 (fr) * 1988-07-26 1993-10-06 Siemens Aktiengesellschaft Chaudière à vapeur à passage unique
EP0503116B2 (fr) * 1991-03-13 1997-11-19 Siemens Aktiengesellschaft Tube avec plusieurs nervures hélicoidales sur sa paroi interne et générateur de vapeur en faisant usage
JP3091220B2 (ja) * 1991-04-18 2000-09-25 シーメンス アクチエンゲゼルシヤフト ほぼ垂直に配置された管から成る垂直煙道を備えた貫流ボイラ
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9607053A1 *

Also Published As

Publication number Publication date
DE59502913D1 (de) 1998-08-27
ES2119461T3 (es) 1998-10-01
CN1155326A (zh) 1997-07-23
JP3046890U (ja) 1998-03-24
WO1996007053A1 (fr) 1996-03-07
KR100368516B1 (ko) 2003-03-15
US5979370A (en) 1999-11-09
KR970705724A (ko) 1997-10-09
CN1107202C (zh) 2003-04-30
EP0778932B1 (fr) 1998-07-22
DE4431185A1 (de) 1996-03-07

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