US3301224A - Steam generator organization - Google Patents

Steam generator organization Download PDF

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Publication number
US3301224A
US3301224A US513222A US51322265A US3301224A US 3301224 A US3301224 A US 3301224A US 513222 A US513222 A US 513222A US 51322265 A US51322265 A US 51322265A US 3301224 A US3301224 A US 3301224A
Authority
US
United States
Prior art keywords
furnace
tubes
walls
wall
flue
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
US513222A
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English (en)
Inventor
Alwin W Ambrose
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.)
Combustion Engineering Inc
Original Assignee
Combustion Engineering Inc
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 Combustion Engineering Inc filed Critical Combustion Engineering Inc
Priority to US513222A priority Critical patent/US3301224A/en
Priority to GB50521/66A priority patent/GB1152340A/en
Priority to DE6605312U priority patent/DE6605312U/de
Priority to DE19661551007 priority patent/DE1551007A1/de
Priority to BE690627D priority patent/BE690627A/xx
Priority to FR86156A priority patent/FR1503253A/fr
Priority to ES334268A priority patent/ES334268A1/es
Priority to NL6617259A priority patent/NL6617259A/xx
Application granted granted Critical
Publication of US3301224A publication Critical patent/US3301224A/en
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
    • F22B29/061—Construction of tube walls
    • F22B29/062—Construction of tube walls involving vertically-disposed water 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
    • F22B29/02—Steam boilers of forced-flow type of forced-circulation type
    • F22B29/023—Steam boilers of forced-flow type of forced-circulation type without drums, i.e. without hot water storage in the boiler
    • F22B29/026—Steam boilers of forced-flow type of forced-circulation type without drums, i.e. without hot water storage in the boiler operating at critical or supercritical pressure

Definitions

  • the pressure drop through the steam generator affects the cycle efliciency, and it is therefore desirable to design the steam generator with the minimum pressure drop consistent with other design considerations.
  • One of these design considerations is the protection of a furnace wall tubing in the lower furnace or burner zone. In order to achieve satisfactory cooling of the tubing materials in this area, minimum safe mass flow rates must be maintained. In other areas of the steam generator, however, the heat absorption rates are considerably lower and, accordingly, lower mass flow rates are tolerable for safe conditions.
  • the mass flow rate throughout the length is the same if the tube maintains the same inside diameter.
  • Another object of the invention is to provide an improved once-throug-h flow vapor generator operating at supercritical pressures and provided with tubular panel wall type furnace wall construction in which the stresses within the panel are maintained at a relatively low value.
  • a further object is to provide an improved once-through flow supercritical vapor generator having decreased temperature unbalance in the tubes leaving the furnace wall structure and, accordingly, permitting the furnace walls to be designed for lower temperatures :at this outlet portion.
  • the invention comprises an arrangement, construction and combination of the elements of the inventive organization in such a manner :as to attain the results desired, as hereinafter more particularly set forth in the following detailed description of an illustrative embodiment, said embodiment being shown by the accompanying drawings wherein:
  • FIG. 1 is a side elevation of a vapor generator employing the instant invention
  • FIG. 2 is an isometric view of the tubing headers and piping of relevant portions of the vapor generator
  • FIG. 3 is a sectional view through the tubes lining the lower portion of the furnace taken at section 33;
  • FIG. 4 is a sectional view through the tubes lining the upper walls of the furnace and the tubes lining the walls of the flue taken through section 44.
  • tubes 32 lining the walls of the flue 26 also receive fluid from the ring header 24 and convey it to the furnace wall outlet header 3t). From this point the through-flow is conveyed to the panel inlet header 34 passing through the superheater panel 36 for initial superheating. This throughflow is then serially passed through superheater sections 38, 4t), 42 and 44 reaching its full degree of superheat as it enters superheater outlet header 46. From this point the steam is conveyed to a steam turbine (not shown) which is used for the generation of electric power.
  • Fuel is fired tangentially into the furnace 22 through burners 56 with the combustion gases passing upwardly through the furnace over panels 36 and heating surfaces 52 and 44. These gases pass through the furnace outlet formed in the rear wall where the tubes at the upper portion are offset to permit the gas egress. These combustion gases then pass downwardly through the flue 26 over heating surfaces 40, 38, 5t and 4 with these gases passing out through exhaust duct 58 to an air heater (not shown).
  • the temperature of each of these tubes will vary as it delivers fluid to the header 24.
  • the fluid is generally mixed before delivering it to the upper furnace tubes 28.
  • This mixing is improved in this header system since the ring header 24 receives fluid only in that portion adjacent the furnace 22 while it delivers fluid to the area of both the furnace and the vertical fine 26. Accordingly, a cross how is developed in this header which improves the mixing of the various streams which are entering the header. Due to this mixing the temperature unbalance entering the tubes 28 is decreased and, accordingly, the temperature unbalance leaving these tubes is decreased. Therefore, the design temperature of these tubes may be lower than it would be without the mixing.
  • the tube sizing of the tubes lining the lower furnace wall as indicated in FIG. 3 is selected to supply adequate mass flow rates in this burner zone where heat absorption rates are extremely high.
  • the tubes are 1% inches in diameter with /2 inch webs 60 welded to adjacent tubes. Such mass flow rates are not required in either the upper furnace portion or the flue 26.
  • FIG. 4 illustrates the tubing selection employed in these low heat absorption rate locations.
  • the upper furnace walls are covered with 1 /2 inch tubes 28 having 1 inch webs 62 welded therebetween.
  • the wall tubes are of 2 inch diameter tubing with 4 inch webs 63 welded between adjacent tubes.
  • the total flow area of all the tubes lining the walls of the flue plus those lining the walls of the upper furnace is greater than the flow area of the tubes lining the lower furnace wall. This results .in lower mass fiow rates and, accordingly, lower pressure drop. Since the perimeter supplied from header 24 is substantially greater than the perimeter of the lower furnace, increased tube spacing may be employed in the upper sections. The spacing between the tubes is covered by an increased length of fin between the adjacent tubes. Fin length is also limited as a function of the heat exchange rate of any particular section since excessive fin lengths will result in high fin temperatures with their ultimate destruction. Since lower heat absorption rates occur in these upper zones, increased fin lengths can be tolerated.
  • the upper furnace wall tubes as compared to those of the lower furnace provide an increased spacing between the outer edges of adjacent tubes. This facilitates the passage of the superheater tubes going to and from the superheater sections 38 and 44 as well as reheater section 52 as they pass through the furnace wall since it reduces the amount of offsetting of the furnace wall tubes required to pass the tubes through.
  • the tubes 20 and 28 lining the lower and upper portions respectively of the furnace 22 are formed into welded panels by welding web between adjacent tubes 20 in the lower furnace and welding web 62 between the adjacent tubes 28 in the upper furnace.
  • This welded wall construction is well known as well as its advantages of simplified erection with good gas-tight construction. Obviously, when temperature differences exist between welded tubes in such a construction, stresses are set up within the structure. These stresses are minimized on this construction because of the mixing achieved and, accordingly, reduction of temperature difference between parallel tubes-
  • the rear wall of the furnace is formed at its upper sec tion by tubes 28 with these tubes also comprising the front wall of the flue 26. With such a structure the side walls of each section, that is, the upper portion of the furnace 22 and the flue 26, are welded together.
  • Recirculating line 64 including stop check valve 66 is operative to recirculate a portion of the fiow entering the furnace wall outlet header 30 through line 64 in parallel with tubing sections 20, 28 and 32 so that this amount of flow may be passed through these tubes in supplement to the through-flow.
  • a system is described in 11.8. Patent No. 3,135,252, issued June 2, 1964 to W. W. Schroedter. This recirculation system further decrease the temperature unbalance between tubes, thereby further decreasing any stresses incurred by that temperature difference.
  • An apparatus as in claim 3 having also a circulating system superimposed on the through-flow system in parallel flow relation with the tubes lining the furnace walls and the tubes lining the flue walls and effective to recirculate working medium through these portions of the through-flow system in supplement to the through-flow.

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  • 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)
US513222A 1965-12-13 1965-12-13 Steam generator organization Expired - Lifetime US3301224A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US513222A US3301224A (en) 1965-12-13 1965-12-13 Steam generator organization
GB50521/66A GB1152340A (en) 1965-12-13 1966-11-10 Forced-Through-Flow Type Vapor Generator
DE19661551007 DE1551007A1 (de) 1965-12-13 1966-12-01 Durchlaufdampferzeuger
DE6605312U DE6605312U (de) 1965-12-13 1966-12-01 Durchlaufdampferzeuger
BE690627D BE690627A (enrdf_load_html_response) 1965-12-13 1966-12-02
FR86156A FR1503253A (fr) 1965-12-13 1966-12-05 Générateurs de vapeur à traversée unique
ES334268A ES334268A1 (es) 1965-12-13 1966-12-07 Un generador de vapor.
NL6617259A NL6617259A (enrdf_load_html_response) 1965-12-13 1966-12-08

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US513222A US3301224A (en) 1965-12-13 1965-12-13 Steam generator organization

Publications (1)

Publication Number Publication Date
US3301224A true US3301224A (en) 1967-01-31

Family

ID=24042352

Family Applications (1)

Application Number Title Priority Date Filing Date
US513222A Expired - Lifetime US3301224A (en) 1965-12-13 1965-12-13 Steam generator organization

Country Status (7)

Country Link
US (1) US3301224A (enrdf_load_html_response)
BE (1) BE690627A (enrdf_load_html_response)
DE (2) DE6605312U (enrdf_load_html_response)
ES (1) ES334268A1 (enrdf_load_html_response)
FR (1) FR1503253A (enrdf_load_html_response)
GB (1) GB1152340A (enrdf_load_html_response)
NL (1) NL6617259A (enrdf_load_html_response)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080104960A1 (en) * 2006-11-07 2008-05-08 H2Gen Innovations, Inc. Heat exchanger having a counterflow evaporator
US20110139092A1 (en) * 2008-09-17 2011-06-16 Junji Imada Reheat boiler
US20130264827A1 (en) * 2010-06-16 2013-10-10 Chao Hui Chen Steam Generator
WO2017088742A1 (zh) * 2015-11-25 2017-06-01 东方电气集团东方锅炉股份有限公司 一种低负荷下高流动稳定性的超临界循环流化床锅炉水冷壁及实现低质量流速的方法

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5623603A (en) * 1979-08-01 1981-03-06 Mitsubishi Heavy Ind Ltd Forced flowinggthrough boiler
DE3447265A1 (de) * 1984-12-22 1986-06-26 L. & C. Steinmüller GmbH, 5270 Gummersbach Verfahren und vorrichtung zur erzeugung von hochgespanntem und ueberhitztem dampf
JPH0448105A (ja) * 1990-06-18 1992-02-18 Mitsubishi Heavy Ind Ltd 変圧貫流ボイラ火炉蒸発管
DE4431185A1 (de) * 1994-09-01 1996-03-07 Siemens Ag Durchlaufdampferzeuger

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125995A (en) * 1964-03-24 forced flow vapor generating unit
US3162179A (en) * 1962-12-05 1964-12-22 Gilbert Associates Fluid circulation system for a oncethrough type steam generator
US3221713A (en) * 1963-08-20 1965-12-07 Babcock & Wilcox Co Forced flow vapor generator

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125995A (en) * 1964-03-24 forced flow vapor generating unit
US3162179A (en) * 1962-12-05 1964-12-22 Gilbert Associates Fluid circulation system for a oncethrough type steam generator
US3221713A (en) * 1963-08-20 1965-12-07 Babcock & Wilcox Co Forced flow vapor generator

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080104960A1 (en) * 2006-11-07 2008-05-08 H2Gen Innovations, Inc. Heat exchanger having a counterflow evaporator
US7882809B2 (en) * 2006-11-07 2011-02-08 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger having a counterflow evaporator
US20110139092A1 (en) * 2008-09-17 2011-06-16 Junji Imada Reheat boiler
US20130264827A1 (en) * 2010-06-16 2013-10-10 Chao Hui Chen Steam Generator
US9429313B2 (en) * 2010-06-16 2016-08-30 Doosan Babcock Limited Steam generator
WO2017088742A1 (zh) * 2015-11-25 2017-06-01 东方电气集团东方锅炉股份有限公司 一种低负荷下高流动稳定性的超临界循环流化床锅炉水冷壁及实现低质量流速的方法

Also Published As

Publication number Publication date
NL6617259A (enrdf_load_html_response) 1967-06-14
BE690627A (enrdf_load_html_response) 1967-06-02
DE6605312U (de) 1970-05-06
GB1152340A (en) 1969-05-14
FR1503253A (fr) 1967-11-24
ES334268A1 (es) 1968-02-01
DE1551007A1 (de) 1970-01-29

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