US3343523A - Vapor generator - Google Patents

Vapor generator Download PDF

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Publication number
US3343523A
US3343523A US501269A US50126965A US3343523A US 3343523 A US3343523 A US 3343523A US 501269 A US501269 A US 501269A US 50126965 A US50126965 A US 50126965A US 3343523 A US3343523 A US 3343523A
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United States
Prior art keywords
pass
furnace
tubes
enclosure
passes
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Expired - Lifetime
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US501269A
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English (en)
Inventor
Walter P Gorzegno
Cooper Jacob
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Foster Wheeler Inc
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Foster Wheeler Inc
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Priority to US501269A priority Critical patent/US3343523A/en
Priority to ES0332347A priority patent/ES332347A1/es
Priority to GB47412/66A priority patent/GB1163555A/en
Priority to FR80976A priority patent/FR1515034A/fr
Application granted granted Critical
Publication of US3343523A publication Critical patent/US3343523A/en
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    • 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

  • This invention relates to a forced-flow supercritical and subcritical once-through vapor generating unit.
  • the invention relates to a furnace circuit arrangement for forced-flow units in which the furnace tubes are vertically aligned in parallel and adjacent tubes are fin-welded along their length to form a gas-tight, tubular panel wall, furnace enclosure.
  • each pass section comprising parallel finned tubes welded along their lengths into vertically oriented panels.
  • Inlet and outlet headers serve each pass section separately, and are connected so that the flow in the enclosure Wall is in series through the successive pass sections. Since the temperature of the fluid increases from the first to the last pass section, the pass sections are arranged so that the intermediate section is divided into two panels operating in parallel and disposed between the panels of the first and last sections.
  • the panels for all the pass sections are welded together as with the tubes, so that the enclosure is gas tight.
  • the flow in tubes of a pass section is made sufficiently uniform to avoid tube overheating and limit fatigue causing temperature fluctuations in any one pass.
  • a temperature differential will exist between adjacent welded tubes of adjacent pass sections, but, in accordance with the invention, the arrangement of the intermediate pass section panels between the first and last section panels achieves a temperature differential between tubes of the different pass sections less than 100 F. and acceptable with respect to weld and tube strength design criteria.
  • FIGURE 1 is an oblique expanded View of a subcn'tical forced-flow once-through vapor generator in accordance with the invention
  • FIGURE 2 is a side elevation view of the generator of FIG. 1;
  • FIGURE 3 is a further exploded view showing in detail elements of the generator of FIG. 1;
  • FIGURE 4 is a section of the panel wall of the generator of FIG. 1;
  • FIGURE 5 is a temperature vs. enthalpy diagram for the subcritical generator of FIGS. 14 for maximum continuous load at 3.547 million pounds of steam per hour;
  • FIGURE 6 is an oblique expanded view of a forcedflow once-through vapor generating supercritical unit in accordance with an embodiment of the invention.
  • the vapor generator includes a furnace 12 for a forced circulation steam generating unit which has a rectangular horizontal cross-section and is vertically orientated.
  • Burners 14 and 16 (schematically indicated in FIG. 1) are disposed in the lower portion of the furnace enclosure in the front furnace wall 18 and rear furnace wall 20 respectively.
  • the front and side walls continue upwardly to define an upper portion 22 of the furnace enclosure, from which a gas pass above the rear wall 20 leads to the convection portion 23 of the generator.
  • the flue gases from the combustion of a suitable fuel leave the furnace enclosure by passing over a furnace exit screen 24 flowing, in cross-flow relationship, first over a platen superheater 26 in the high heat absorption area of the upper furnace (in front of screen 24) and then over the finishing superheater bank 27 between the front screen 24 and a rear screen 28.
  • the convection section of the unit includes an economizer pass 30, a reheater pass 32, and a primary superheater pass 34.
  • the flue gases exiting the convection section flow through an air heater and to the stack (not shown).
  • the high pressure fluid flow circuitry routing through the furnace enclosure of the unit consists of five series connected pass sections joined through mixing headers.
  • floor pass No. l, and upflow passes Nos. 2, 3 and 4 form the floor and enclosure walls in the lower portion of the furnace
  • upflow pass No. 5 forms the enclosure walls in the upper portion of the furnace. All furnace tubes are Welded along their lengths as shown in FIG. 4 forming fin-welded panels and a gas-tight construction.
  • feed water enters inlet 30a to the economizer 30 (which is disposed in the flue gas passages therefor) and flows from the economizer via two downcomer pipes 30b to feed the furnace floor pass No. 1, item 36.
  • the fluid from floor pass No. l is transmitted then to an inlet header 38a feeding the tubes of pass No. 2 (item 38) comprising a substantial portion of the front wall 18.
  • the fluid flows in parallel downcomers 39 to the separated L-shaped headers 40a feeding opposed third pass panels, items 40.
  • These L-shaped panels make up the remainder of the front Wall 18 on opposite sides of the second pass panel 38, and more than half of each side wall.
  • the fluid from furnace pass No 3 exits via opposed upper L-shaped headers 40b to downcomers 41 feeding a lower U-shaped header 42a which constitutes the inlet for U-shaped panel of pass No. 4 (item 42).
  • This panel makes up the rear portions or remainder of the side walls and the rear wall.
  • a mixing bottle 43 assures a uniform enthalpy flow to the fourth pass lower header.
  • fluid is transmitted by risers 44 to a U- shaped header 46a feeding the fifth pass 46.
  • This pass makes up the side and front walls of the upper portion of the furnace enclosure, with U-shaped outlet header 46b also serving the pass.
  • a plurality of riser tubes 47 transmit the flow to opposite downcomers 48 leading to Ts 50 (on opposite sides of the boiler), from which lines 52 and 54 transmit the flow in desired proportions to (a) the enclosure for pendant finishing superheater 27, and (b) the enclosures for the convection section, economizer, reheater and superheater passes 30-34, respectively.
  • the flow in line 52 divides into lines 56 and 58 feeding the front and rear screen tubes 24- and 28 and the enclosure side walls 60, respectively.
  • the flow feeds the rectangular shaped header 62 near the convection pass outlet.
  • This header is provided with a cross-pipe 64 which feeds the division wall 66 for the convection pass. From all of these passes, the flow leadsto a common header 68 at the top of the unit.
  • risers 70 feed inlet header 72 for the roof tubes 74, the fluid flowing in sequence to outlet header 76 for the roof tubes, to the primary superheater 34 via inlet header 78 therefor, and to the platen superheater 26 via outlet header 80 for the primary superheater and inlet header 82 for the platen superheater.
  • Item 84 is the outlet header for the platen superheater and feeds the finishing superheater bank 27 exiting at header 86.
  • the reheater 32 is fed by inlet header 90, with flow countercurrent to the gas flow to outlet headers 92 and 94.
  • Division of the furnace periphery into a plurality of passes in series limits the extent of flow unbalance which can occur in these forced flow circuits by virtue of heat absorption variation.
  • the furnace enclosure is made up of a single circuit between mix headers, such factors as unbalances in firing, difierences in tube lengths, and slag deposition can cause severe flow variations in this multi-tube circuit. Severe flow unbalance in such a single circuit would then cause inadequate cooling and overheating of some tubes.
  • a particularly critical area in the furnace circuitry is the mixture (steam and water) cooled region of the circuitry.
  • a continuous steam film may cover the inside of the tube wall causing departure from desired nucleate boiling and resulting in a low heat transfer rate to the fluid. This in turn results in tube overheating. Maintaining nucleate boiling depends in part on maintaining a turbulentflow in the tubes.
  • the multiple pass design of the invention permits sizing this region or pass so that a predetermined minimum flow rate is maintained in the tubes of the pass.
  • a turbulator device (disposed in tube lengths as shown in FIG.
  • the present invention is an improvement in dividing the enclosure into a plurality of in-series passes each with a lesser enthalpy pickup.
  • the arrangement of passes permits dividing the furnace vertically, in its longitudinal direction, into upper and lower portions with the high absorption area passes Nos. 2, 3, and 4 terminating about half way up the furnace and being of approximate equal length.
  • the enthalpy pick-up per pass would be high, and those tubes in the rear wall would be of different length than the tubes of the remainder of the enclosure (to provide a passageway for the furnace gases to the convection section of the unit), both factors contributing to the tendency to maldistribution of flow.
  • the mix headers between lower pass No. 4 and upper pass No. 5 are about halfway up the furnace, but are located sufiiciently high up to have a heat input into the upper pass reduced to the extent that the tubes of the upper passes with lower fluid mass flow rates can be still properly cooled.
  • the firing is by opposite rows of burners in the front and rear walls. Because of the arrangement of the lower furnace passes, and the limited fluid enthalpy pick-up of all furnace passes, this design can tolerate significant firing unbalance without detrimental effect. For example, a front to back firing unbalance will increase overall absorption in the front or rear wall pass but will not significantly upset absorption in any given pass to cause damaging circuit flow unbalance. However, in this subcritical design, the front to back firing unbalance should not exceed that which would cause a steam water mixture entering pass No. 4 to exceed 8% steam by weight. For balanced firing this fluid is a subcooled single phase entering pass No. 4.
  • a side to side firing unbalance will cause an upset absorption for all furnace passes, in particular the side walls (pass N0. 3), but because of the limited pass fluid enthalpy pick-up, a significant absorption upset will only cause a minor unbalancing of circuit flow.
  • the use of a plurality of passes in series in the furnace enclosure as described allows and in fact requires the use of larger tubes than conventional in once-through boilers.
  • the mass flow rate (lbs./hour/sq. ft.) per tube is correspondingly increased.
  • the need for larger tube diameters is apparent.
  • the tubes are all 1% inch CD. (which is large for a once-through boiler) with .180 to .200 inch minimum wall thickness, on 1 /2 inch centers.
  • the use of larger tubes, which are relatively stiffer makes it easier to weld the tubes into panels, makes it easier to design and install turbulators, and has other advantages, which in turn achieve economies in construction of the unit.
  • the pass is designed with as large a number of tubes as possible (consistent with maintaining minimum mass flow in the pass).
  • the tubes of passes Nos. 2 and 3 make up as little of the furnace periphery as possible.
  • the enthalpy pick-up in the circuit-up to pass No. 4 is less than that which will with balanced firing create a steam and water phase at the inlet to this pass.
  • a mass flow of X 10 lbs./hr./sq. ft is considered minimum in a tube in pass No. 4 in the high heat absorption zone of the furnace.
  • the disposition of tubes in enclosure passes Nos. 2-4 assures that a water phase enters this pass.
  • the number of tubes in pass No. 4 is sufliciently restricted to assure that at least the minimum mass flow is obtained in the tubes of this pass.
  • the number of tubes in the floor pass No. 1 is of course dictated by the width of the unit.
  • the steam generator illustrated is top supported by suitable steel members (not shown) permitting free expansion.
  • the furnace upper tubular elements (of passes Nos. 4 and 5) are suspended from the top, and the lower passes are suspended from the upper passes by interconnecting adjacent tubular elements of the respective passes in the manner set forth in TABLE I Heat Pick-up Btu/lb. Fluid Outlet Temp, F. Location No. of 100% 100% 30% Tubes Load Load Load Load Pass No. l Floor 429 585 525 Front Wall 382 80 640 605 Front and Side Walls- 390 80 680 665 Side and Rear Walls 664 135 180 695 67 5 Pass No.
  • FIG. 6 illustrates principles of the invention specifically for a supercritical steam generator, wherein the numbers 112 and 114 represent the furnace and convection enclosures respectively, the latter containing economizer 116.
  • economizer 116
  • downcomers 118 lead to the ends of a I-shaped header 120, the stem of which feeds a wall of tubes 122 which makes up the front slopping hopper pass 124 of the furnace and the lower part of the front Wall 126.
  • the legs of the header feed opposed tubes 124 which make up a portion of each side wall of the furnace.
  • the tubes comprising these side wall portions and the front Wall are integrally joined to form a U-shaped panel constituting pass No.
  • the fluid flows downward through two external downcomers 140 into a U-shaped entrance header 142 for pass No. 3.
  • the tubes of pass No. 3 extend therefrom and form a U-shaped panel 144 comprising the lower part of the rear wall 146 and portions 148 of the side walls adjacent thereto.
  • the fluid flows upward through the tubes of pass No. 3 and feeds into U-shaped exit header 150.
  • This panel is welded to b tubes of the pass No. 2 panel so that the entire enclosure is gas tight.
  • the fluid routes to a U-shaped inlet header 152 of furnace pass No. 4 via piping 154.
  • the tubes of pass No. 4 extend upward from header 152 and make up the entire side walls and front Wall of the upper furnace region.
  • the fluid exits through downcomers 158 to feed inlet header 160 for a pass No. 5, which forms the upper part of the rear wall 162 of the upper furnace enclosure, and the pendant vestibule enclosure for the superheater bank 168. It comprises furnace exit screen 170, rear screen 172 and the side and bottom walls 174 and 176, respectively, of the enclosure.
  • pass No. 5 the fluid is routed through a suitable downcomer to feed pass No. 6 which includes the front, rear, side, and partition walls of the enclosure 114 for the horizontally oriented convection surface.
  • pass No. 6 which includes the front, rear, side, and partition walls of the enclosure 114 for the horizontally oriented convection surface.
  • Ser. No. 370,604 filed on May 3, 1962. Since pass No. 5 is aligned above, and supports pass No. 3, a minimum temperature differential between tubes of the upper and lower furnace passes is achieved, than would be the case if the lower (or upper) furnace passes were reversed and pass Nos. 1 and 5 were adjacent.
  • pass No. 5 as described above, may be extended to encompass a portion of the furnace periphery occupied by pass No. 4, thereby reducing the periphery of the furnace cooled by pass No. 4, and permitting the mass flow rate in this pass to be increased.
  • suitably sized pipe connections are used to connect the multiple passes, the pass outlet and inlet headers being properly sized to limit fluid flow unbalance caused by velocity head and pressure drop variations in these headers.
  • the passes are sized to keep maximum fluid flow velocity in the tubes of those passes where it is most needed.
  • the fluid passes in the furnace walls are arranged to assure that flow velocities within the tubes are kept highest at locations where maximum heat absorption is obtained.
  • a high absorption zone such as the lower furnace
  • Metal temperatures are kept low (note FIG. 5) thereby circumventing the use of expensive alloy steels.
  • pass No. 1 has more tubes than pass No. 2 which in turn has more tubes than pass No. 3.
  • mass flow is greatest in progressively succeeding lower furnace tubes to lower the steam film temperature drop to compensate for higher bulk fluid temperature in the succeeding passes.
  • pass No. 4 is sized with a larger number of tubes and has a lower fluid mass flow rate.
  • the passes are designed for optimum fluid cooling, mass flow1bs./hr.square feet-to effect eflicient cooling of the tube metal to low design metal temperatures whereby minimum fluid pressure drop may be" achieved.
  • Representative mass flows are asfollows:
  • each furnace pass is restricted to a portion of the furnace walls, and has low enthalpy pick-up, the temperature differentials between different passes at various loads are maintained within satisfactory limits even with extreme unbalanoes in firing, allowing a maximum tolerance for uneven heat absorption around the periphery of the furnace.
  • the difference of temperature between adjacent tubes of dilferent passes exceed 100 F.
  • resulting metal stresses are kept to accepted values.
  • these pass joints occur only at certain locations and are few in number. Temperature differentials between tubes of the same pass are nil, and excursions of tube metal temperatures in a given furnace wall area because of upset absorption cannot be experienced to any great extent.
  • the lower furnace passes having different bulk fluid temperatures terminated away from the corners of the furnace enclosure.
  • Subcritical units require that a much greater amount of the furnaceperiphery be taken up by the last lower furnace pass. In such units, excessive front to back absorption unbalance is not desirable to avoid raising the enthalpy of the fluid to the point where there is a steam and water mixture entering the last lower furnace pass.
  • provisions are made in the connections to this steam-water pass inlet to permit up to 8% steam by weight fluid mixtures to enter without exceeding design margins.
  • a supercritical unit does not have this front to back absorption upset limitation. Accordingly, in subcritical units, the respective passes in the lower furnace are sized to avoid this steam-water condition entering the last pass in the lower furnace.
  • the lower furnace enclosure passes are sized to achieve progressively greater flow rates per tube, with the tubes of pass No. l exceeding in number those of pass No. 3. HoW-. ever, in some designs the lower furnace passes may be sized for equal fluid mass flow rates.
  • the side to side unbalances in subcritical units are provided for in the same manner as in the supercritical units.
  • the Buffer Circuit of copending application Ser. No. 501,168, filed Oct. 22, 1965 by Walter P. Gorzegno may be used in either the subcritical or supercritical designs.
  • a once-through vapor generator comprising a rectangular vertically oriented furnace enclosure
  • the enclosure comprising side-by-side panel sections defining at least three upflow flo-w passes;
  • each panel section comprising parallel vertically oriented finned tubes welded together;
  • the panel sections being welded together so that the enclosure is essentially gas-tight; burner means radiantly heating said enclosure; header means connecting the flow passes in series, the enthalpy of the fluid increasing in successive passes;
  • the panel sections being arranged whereby an intermediate enthalpy pass comprising multiple panel sections is disposed on opposite sides of and intermediate the panel sections of the higher and lower enthalpy passes.
  • a once-through vapor generator comprising Wall means defining a rectangular radiant heating section
  • the wall means comprising a plurality of parallel finned tubes welded together longitudinally to define an essentially gas tight enclosure
  • the tubes and headers therefor being arranged so that the enclosure is divided into at least four side-byside panel sections, the panel sections being connected in series to form at least three upflow fluid passes of increasing enthalpy;
  • burner means radiantly heating said wall means
  • the intermediate pass of intermediate enthalpy comprising at least two of said panel sections wherein the two panel sections separate and are on opposite sides of the remaining two panel sections of the passes of higher and lower enthalpy.
  • a once-through vapor generator comprising four side-by-side vertically oriented panel sections welded together to form a rectangular furnace enclosure;
  • each panel section comprising parallel vertically ori-.
  • burner means radiantly heating said enclosure
  • the intermediate pass of intermediate enthalpy comprising t-wo of said panel sections wherein the two panel sections separate and are on opposite sides of the remaining two panel sections of the passes of higher and lower enthalpy.
  • the panels of the lower and intermediate enthalpy passes occupying a limited portion of the furnace enclosure so that a water phase enters the higher enthalpy pass.
  • a vapor generator according to claim 4 wherein the arrangement of panel sections in the enclosure is symmetrical.
  • a vapor generator according to claim 4 which includes turbulators in the higher enthalpy pass tubes.
  • a vapor generator according to claim 3 wherein the side-by-side panel sections occupy a lower portion only of the furnace enclosure, further including a further upfiow pass comprising front and side wall panel sections occupying the upper portion of the furnace enclosure;
  • the tubes having approximately 1% inches OD.
  • a once-through vapor generator comprising first wall means defining a furnace radiant heating section
  • the second wall means defining a convection section in gas flow communication with the furnace section;
  • the first wall means comprising at least four side-byside panel sections, each panel section comprising parallel finned tubes welded longitudinally together,
  • a forced-flow once-through vapor generator comprising;
  • means defining a lower furnace chamber said means including a plurality of panels formed together each having substantially vertical oriented parallel upflow tubes welded together along their length to form a gas-tight lower furnace enclosure;
  • the enclosure comprising a first flow pass, a last flow pass, and at least one intermediate flow pass arranged in series flow, with the first and last flow pass;
  • the intermediate flow pass comprising two such panels disposed in spaced relationship from each other along the periphery of the enclosure and between the immediately preceedin'g and succeeding series arranged fiow pass panels;
  • mixing means between the passes arranged to receive and mix all the flow from each pass;
  • a forced-flow vapor generator of claim 14 wherein the panels form a rectangular enclosure and are adapted so that the vertical edges of adjacent pass panels are not coincident with the corners of said enclosure.
  • a forced-flow vapor generator of claim 14 where in the generator is designed for supercritical pressures, succeeding series passes comprising progressively increasing numbers of tubes, the number of tubes in each pass being selected so as to optimize the pressure drop and mass fluid flow therethrough.
  • a forced-flow vapor generator of claim 14 further comprising two separate inlet headers and two separate outlet headers respectively arranged to pass flow into and out of the two panels of the intermediate fiow pass.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US501269A 1965-10-22 1965-10-22 Vapor generator Expired - Lifetime US3343523A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US501269A US3343523A (en) 1965-10-22 1965-10-22 Vapor generator
ES0332347A ES332347A1 (es) 1965-10-22 1966-10-17 Un generador de vapor de tipo directo.
GB47412/66A GB1163555A (en) 1965-10-22 1966-10-21 Once through vapor generators
FR80976A FR1515034A (fr) 1965-10-22 1966-10-21 Générateur de vapeur

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US501269A US3343523A (en) 1965-10-22 1965-10-22 Vapor generator

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US3343523A true US3343523A (en) 1967-09-26

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US501269A Expired - Lifetime US3343523A (en) 1965-10-22 1965-10-22 Vapor generator

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GB (1) GB1163555A (es)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3406664A (en) * 1966-12-29 1968-10-22 Combustion Eng Waste heat boiler
US3556059A (en) * 1969-01-28 1971-01-19 Foster Wheeler Corp Two-pass furnace circuit arrangement for once-through vapor generator
US3771498A (en) * 1972-01-03 1973-11-13 Foster Wheeler Corp Furnace circuit for variable pressure once-through generator
US3872836A (en) * 1973-09-18 1975-03-25 Foster Wheeler Corp Coal-fired generator of medium to large capacity
US4294200A (en) * 1979-12-06 1981-10-13 Foster Wheeler Energy Corporation Variable pressure vapor generator utilizing crossover circuitry for the furnace boundary wall fluid flow tubes
EP1793163A1 (de) * 2005-12-05 2007-06-06 Siemens Aktiengesellschaft Dampferzeugerrohr, zugehöriges Herstellungsverfahren sowie Durchlaufdampferzeuger

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0352488B1 (de) * 1988-07-26 1993-10-06 Siemens Aktiengesellschaft Durchlaufdampferzeuger

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2989036A (en) * 1954-04-28 1961-06-20 Duerrwerke Ag Once-through vapor generating and superheating units
US3159146A (en) * 1960-08-19 1964-12-01 Steinmueller Gmbh L & C Water-cooled suspension of steam producers
US3162179A (en) * 1962-12-05 1964-12-22 Gilbert Associates Fluid circulation system for a oncethrough type steam generator
US3247830A (en) * 1962-06-08 1966-04-26 Sulzer Ag Forced flow steam generator having plural tube systems

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2989036A (en) * 1954-04-28 1961-06-20 Duerrwerke Ag Once-through vapor generating and superheating units
US3159146A (en) * 1960-08-19 1964-12-01 Steinmueller Gmbh L & C Water-cooled suspension of steam producers
US3247830A (en) * 1962-06-08 1966-04-26 Sulzer Ag Forced flow steam generator having plural tube systems
US3162179A (en) * 1962-12-05 1964-12-22 Gilbert Associates Fluid circulation system for a oncethrough type steam generator

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3406664A (en) * 1966-12-29 1968-10-22 Combustion Eng Waste heat boiler
US3556059A (en) * 1969-01-28 1971-01-19 Foster Wheeler Corp Two-pass furnace circuit arrangement for once-through vapor generator
US3771498A (en) * 1972-01-03 1973-11-13 Foster Wheeler Corp Furnace circuit for variable pressure once-through generator
US3872836A (en) * 1973-09-18 1975-03-25 Foster Wheeler Corp Coal-fired generator of medium to large capacity
US4294200A (en) * 1979-12-06 1981-10-13 Foster Wheeler Energy Corporation Variable pressure vapor generator utilizing crossover circuitry for the furnace boundary wall fluid flow tubes
EP1793163A1 (de) * 2005-12-05 2007-06-06 Siemens Aktiengesellschaft Dampferzeugerrohr, zugehöriges Herstellungsverfahren sowie Durchlaufdampferzeuger
WO2007065791A2 (de) * 2005-12-05 2007-06-14 Siemens Aktiengesellschaft Dampferzeugerrohr, zugehöriges herstellungsverfahren sowie durchlaufdampferzeuger
WO2007065791A3 (de) * 2005-12-05 2007-10-11 Siemens Ag Dampferzeugerrohr, zugehöriges herstellungsverfahren sowie durchlaufdampferzeuger
US20090050307A1 (en) * 2005-12-05 2009-02-26 Joachim Franke Steam Generator Pipe, Associated Production Method and Continuous Steam Generator
AU2006324058B2 (en) * 2005-12-05 2010-10-21 Siemens Aktiengesellschaft Steam generator pipe, associated production method and continuous steam generator

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FR1515034A (fr) 1968-03-01
ES332347A1 (es) 1967-07-16
GB1163555A (en) 1969-09-10

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