EP1141625B1 - Fossilbeheizter durchlaufdampferzeuger - Google Patents

Fossilbeheizter durchlaufdampferzeuger Download PDF

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Publication number
EP1141625B1
EP1141625B1 EP99964411A EP99964411A EP1141625B1 EP 1141625 B1 EP1141625 B1 EP 1141625B1 EP 99964411 A EP99964411 A EP 99964411A EP 99964411 A EP99964411 A EP 99964411A EP 1141625 B1 EP1141625 B1 EP 1141625B1
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EP
European Patent Office
Prior art keywords
steam generator
combustion chamber
evaporator tubes
once
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.)
Expired - Lifetime
Application number
EP99964411A
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German (de)
English (en)
French (fr)
Other versions
EP1141625A1 (de
Inventor
Joachim Franke
Rudolf Kral
Eberhard Wittchow
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Siemens AG
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Siemens AG
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Publication date
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Publication of EP1141625A1 publication Critical patent/EP1141625A1/de
Application granted granted Critical
Publication of EP1141625B1 publication Critical patent/EP1141625B1/de
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
    • F22B21/34—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes grouped in panel form surrounding the combustion chamber, i.e. radiation boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
    • F22B21/34—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes grouped in panel form surrounding the combustion chamber, i.e. radiation boilers
    • F22B21/346—Horizontal radiation boilers

Definitions

  • the invention relates to a once-through steam generator, which has a combustion chamber for fossil fuel, which a vertical gas flue on the heating gas side via a horizontal gas flue is connected downstream, the peripheral walls of the combustion chamber made of gas-tightly welded, vertically arranged Evaporator tubes are formed.
  • the Energy content of a fuel to vaporize one Flow medium used in the steam generator In a power plant with a steam generator, the Energy content of a fuel to vaporize one Flow medium used in the steam generator. It will Flow medium usually in an evaporator circuit guided.
  • the steam provided by the steam generator in turn can be used, for example, to drive a steam turbine and / or provided for a connected external process his. If the steam drives a steam turbine, then usually a generator via the turbine shaft of the steam turbine or operated a work machine. in case of a Generator can the current generated by the generator for Infeed into a network and / or island network provided his.
  • the steam generator can be designed as a continuous steam generator his.
  • a continuous steam generator is from the attachment "Evaporator concepts for Benson steam generators" by J. Franke, W. Köhler and E. Wittchow, published in VGB Kraftwerkstechnik 73 (1993), No. 4, pp. 352-360.
  • At a Pass-through steam generator conducts the heating of as evaporator tubes provided steam generator tubes for evaporation of the flow medium in the steam generator tubes in one one-time run.
  • Continuous steam generators are usually equipped with a combustion chamber executed in vertical construction. This means that the combustion chamber for a flow of the heating medium or heating gas designed in an approximately vertical direction is. On the heating gas side, the combustion chamber can use a horizontal gas flue be connected downstream, the transition from Combustion chamber in the horizontal gas flue a redirection of the heating gas flow takes place in an approximately horizontal flow direction.
  • such combustors generally require due to the temperature-related changes in length of the combustion chamber a scaffold on which the combustion chamber is suspended. This requires considerable technical effort in the Manufacture and assembly of the once-through steam generator, the order the greater the overall height of the once-through steam generator is. This is particularly the case with continuous steam generators the case for a steam flow of more than 80 kg / s Are designed for full load.
  • a high live steam pressure promotes high thermal efficiency and thus low CO 2 emissions from a fossil-fired power plant, which can be fired with hard coal or lignite as fuel, for example.
  • the design of the surrounding wall poses a particular problem the throttle cable or combustion chamber of the once-through steam generator with regard to the pipe wall or material temperatures occurring there in the subcritical pressure range up to the temperature of the surrounding wall of the Combustion chamber essentially on the level of the saturation temperature of water determines when wetting the inner surface the evaporator tubes can be ensured. This is done, for example, by using evaporator tubes achieved a surface structure on the inside exhibit.
  • evaporator tubes achieved a surface structure on the inside exhibit.
  • ribbed inside Evaporator tubes into consideration, their use in a once-through steam generator for example from the article cited above is known.
  • These so-called finned tubes i.e. Tube with a ribbed inner surface, have a special good heat transfer from the inner pipe wall to the flow medium.
  • the invention is therefore based on the object of a fossil-fired To specify continuous steam generators of the type mentioned above, a particularly low manufacturing and assembly cost requires, and temperature differences during its operation between adjacent evaporator tubes Combustion chamber are kept particularly small.
  • the continuous-flow steam generator has a combustion chamber with a number of burners arranged at the level of the horizontal gas flue and is designed in such a way that for each number of evaporator tubes which can be acted upon in parallel with flow medium, the evaporator tubes from the steam flow M (specified in kg / s ) at full load and the sum of the internal cross-sectional areas A (specified in m 2 ), this quotient formed in parallel with flow medium to which flow medium can be applied is less than 1350 (specified in kg / sm 2 ).
  • the invention is based on the consideration that one with special low manufacturing and assembly costs Pass-through steam generator an executable with simple means Should have suspension structure.
  • One with comparative scaffolding to be created with little technical effort the combustion chamber suspension can be accompanied by a particularly low overall height of the once-through steam generator.
  • a particularly low overall height of the once-through steam generator can be achieved by using the combustion chamber in a horizontal design is executed.
  • the burners are at the level of the horizontal gas flue arranged in the combustion chamber wall.
  • the heating gas in approximately horizontal main flow direction through the combustion chamber.
  • the rear region of the combustion chamber is heated comparatively less than the front region of the combustion chamber, as seen on the hot gas side, when the continuous steam generator is operating.
  • an evaporator tube near the burner is heated more than an evaporator tube arranged in a corner of the combustion chamber.
  • the heating in the front area of the combustion chamber can be about three times greater than in the rear area.
  • the continuous steam generator should be designed in such a way that a higher flow rate of the flow medium automatically sets in a comparatively more heated evaporator tube than in a comparatively less heated evaporator tube, which is generally the case when the geodetic pressure drop ⁇ p G (specified in bar) of an evaporator tube with medium heating is a multiple of its frictional pressure loss ⁇ p R (specified in bar).
  • ⁇ p B (given in bar) is a change in the acceleration pressure drop
  • ⁇ Q (given in kJ / s) a change in heating
  • M (given in kg / s) the mass flow
  • K (given in (bar s) / kJ) a constant is.
  • the condition formulated in this inequality indicates that with a constant mass flow, the total pressure loss ⁇ ( ⁇ p G + ⁇ p R + ⁇ p B ) (given in bar) decreases in the case of additional heating ⁇ Q, ie must become mathematically negative.
  • the throughput of the flow medium must increase in a multi-heated evaporator tube compared to a less-heated evaporator tube in accordance with the above inequality.
  • the steam flow M is at full load of the once-through steam generator also as permissible steam generation or as Boiler maximum continuous rating (BMCR), and the is the respective inner cross-sectional area of an evaporator tube related to a horizontal cut.
  • BMCR Boiler maximum continuous rating
  • a number of each connected in parallel Evaporator tubes of the combustion chamber a common one Entry collector system upstream and a common one Outlet collector system for flow medium downstream.
  • a continuous steam generator designed in this embodiment namely enables reliable pressure equalization between a number of evaporator tubes connected in parallel, so that each of the evaporator tubes connected in parallel have the same total pressure drop. This means, that compared to a multi-heated evaporator tube to a less heated evaporator tube according to the above inequality the throughput must increase.
  • the evaporator tubes of the end wall of the combustion chamber are advantageous the evaporator tubes of the surrounding walls, the form the side walls of the combustion chamber, on the flow medium side upstream. This makes cooling particularly favorable the highly heated end wall of the combustion chamber.
  • a further advantageous embodiment of the invention is the inside diameter of a number of evaporator tubes the combustion chamber depending on the respective position of the evaporator tubes selected in the combustion chamber. That way the evaporator tubes in the combustion chamber to a hot gas side Predeterminable heating profile adaptable. With the resultant Influence on the flow through the evaporator tubes are particularly reliable temperature differences at the outlet the evaporator tubes of the combustion chamber are kept low.
  • a multi-start thread on the inside forming ribs advantageously has a number of evaporator tubes a multi-start thread on the inside forming ribs.
  • This is advantageously a Pitch angle ⁇ between a perpendicular to the pipe axis Level and the flanks of those arranged on the inside of the pipe Ribs less than 60 °, preferably less than 55 °.
  • a so-called smooth tube, executed evaporator tube can namely from a certain steam content to that for someone special good heat transfer required wetting of the pipe wall can no longer be maintained. If there is no wetting there may be a dry pipe wall in places.
  • the Transition to such a dry pipe wall leads to a so-called heat transfer crisis with deteriorated heat transfer behavior, so that generally the tube wall temperatures rise particularly sharply at this point.
  • this crisis of heat transfer only contributes to a smooth tube a steam mass content> 0.9, i.e. shortly before the end of the Evaporation, on.
  • a number of the evaporator tubes of the combustion chamber advantageously has Means for reducing the flow of the Flow medium. It turns out to be special favorable if the means are designed as throttle devices are. Throttle devices can, for example, internals in the evaporator tubes, which are in one place inside the Reduce the inner tube diameter of the respective evaporator tube. Means for reducing the Flow in a multi-parallel lines Pipe system as advantageous, through which the evaporator tubes flow medium can be supplied to the combustion chamber. It can the pipe system is also an entry collector system from Evaporator tubes that can be acted upon in parallel with flow medium be upstream. In one line or in several Lines of the line system can, for example Throttle fittings may be provided.
  • the flow of the flow medium through the Evaporator tubes can be adjusted to the throughput of Flow medium through individual evaporator tubes at their respective Bring heating to the combustion chamber. Thereby are additional temperature differences of the flow medium particularly reliable at the outlet of the evaporator tubes kept low.
  • the side walls of the horizontal throttle cable and / or the vertical throttle cable are advantageously made of gas-tight welded together, vertically arranged, each parallel to the flow medium acted upon steam generator tubes.
  • Adjacent evaporator or steam generator tubes are on their Long sides advantageously via metal strips, so-called Fins, welded together gastight. These fins can already in the manufacturing process of the pipes with the Connected pipes and form a unit with them. This unit, formed from a tube and fins, will also referred to as fin tube.
  • the fin width affects the Heat input into the evaporator or steam generator tubes. Therefore the fin width is preferably dependent on the position of the respective evaporator or steam generator tubes in Continuous steam generator to a heating profile that can be specified on the hot gas side customized.
  • a heating profile can be a Typical heating profile determined from experience or a rough estimate, such as a step-like one Heating profile.
  • the suitable selected fin widths is also very different Heating various evaporator or steam generator tubes a heat input in all evaporator or Steam generator pipes can be reached in such a way that temperature differences at the outlet of the evaporator or steam generator tubes are kept particularly low. That way are premature Material fatigue reliably prevented. This points the continuous steam generator has a particularly long service life on.
  • the vertical throttle cable advantageously has a number of Convection heating surfaces, which are approximately perpendicular to the Main flow direction of the heating gas arranged tubes formed are. These pipes of a convection heating surface are for a flow through the flow medium connected in parallel. These convection heating surfaces also become predominantly convective heated.
  • the vertical throttle cable advantageously has an economizer.
  • the burners are advantageously arranged on the end wall of the combustion chamber, that is to say on that side wall of the combustion chamber which lies opposite the outflow opening to the horizontal gas flue.
  • a continuous steam generator designed in this way can be adapted in a particularly simple manner to the burnout length of the fuel.
  • the burn-out length of the fuel is understood to mean the heating gas velocity in the horizontal direction at a specific mean heating gas temperature multiplied by the burn-out time t A of the flame of the fuel.
  • the maximum burn-out length for the respective continuous steam generator results from the steam flow M at full load of the continuous steam generator, the so-called full load operation.
  • the burn-out time t A of the flame of the fuel is in turn the time that, for example, a medium-sized coal dust particle takes to completely burn out at a certain average heating gas temperature.
  • the combustion chamber advantageously at least equal to the burnout length the fuel at full load operation of the once-through steam generator.
  • This horizontal length of the combustion chamber will generally at least 80% of the height of the combustion chamber, measured from the top of the funnel to the top of the combustion chamber.
  • the length L (specified in m) of the combustion chamber is advantageously for a particularly favorable utilization of the combustion heat of the fossil fuel as a function of the steam flow M (specified in kg / s) of the continuous steam generator at full load, the burnout time t A (specified in s) of the flame of the fossil fuel and the outlet temperature T BRK (specified in ° C) of the heating gas from the combustion chamber.
  • the advantages achieved with the invention are in particular in that by the appropriate choice of ratio between the steam flow of the once-through steam generator Full load for a number of evaporator tubes connected in parallel and the inner cross-sectional areas of these evaporator tubes a particularly good adjustment of the flow rate of the flow medium through the evaporator tubes to the heating and almost identical temperatures at the outlet of the evaporator tubes are guaranteed.
  • the through temperature differences thermal stresses between adjacent evaporator tubes remain in the peripheral wall of the combustion chamber when operating the continuous steam generator far below the Values at which, for example, the risk of pipe rips given is. This is the use of a horizontal combustion chamber in a once-through steam generator also with comparative long life possible.
  • the heating gas is also a particularly compact one Design of the continuous steam generator given. This makes possible with integration of the once-through steam generator in a power plant with a steam turbine also very short connecting pipes from the once-through steam generator to the steam turbine.
  • the continuous steam generator 2 according to FIG. 1 is not one assigned power plant, which also comprises a steam turbine plant.
  • the Continuous steam generator for a steam flow at full load of designed at least 80 kg / s.
  • the one in the continuous steam generator 2 generated steam is used to drive the steam turbine, which in turn has a generator to generate electricity drives.
  • the electricity generated by the generator is provided for feeding into a network or an island network.
  • the fossil-fueled continuous steam generator 2 comprises an in horizontal design combustion chamber 4, the hot gas side a vertical throttle cable 8 via a horizontal throttle cable 6 is connected downstream.
  • the peripheral walls 9 of the combustion chamber 4th are made of gas-tight welded, vertically arranged Evaporator tubes 10 are formed, a number of which N can be acted upon in parallel with flow medium S.
  • the side walls 12 of the horizontal throttle cable 6 and 14 of the vertical throttle cable 8 from one another in a gas-tight manner welded, vertically arranged steam generator tubes 16 or 17 be formed. In this case, the steam generator pipes 16 or 17 can be acted upon in parallel with flow medium S.
  • a number of the evaporator tubes 10 of the combustion chamber 4 an inlet header system 18 for Flow medium S upstream and an outlet collector system 20 downstream.
  • Entry collector system 18 includes a number of parallel entry collectors. It is for supplying flow medium S into the inlet header system 18 of the evaporator tubes 10, a line system 19 is provided.
  • the line system 19 comprises several connected in parallel Lines, each with one of the entry collectors of the entry collector system 18 are connected.
  • the evaporator tubes 10 have - as shown in Figure 2 - an inner tube diameter D and ribs on the inside 40, which form a kind of multi-start thread and one Have a rib height R.
  • the pitch angle ⁇ is between a plane 42 perpendicular to the pipe axis and the flanks 44 of the ribs 40 arranged on the inside of the tube are smaller than 55 °. This results in a particularly high heat transfer from the Inner walls of the evaporator tubes 10 to that in the evaporator tubes 10 guided flow medium S and at the same time special low pipe wall temperatures reached.
  • the inner tube diameter D of the evaporator tubes 10 of the combustion chamber 4 depends on the respective position of the evaporator tubes 10 selected in the combustion chamber 4. In this way the continuous steam generator 2 is different strong heating of the evaporator tubes 10 adapted. This interpretation the evaporator tubes 10 ensures the combustion chamber 4 particularly reliable that temperature differences at the outlet the evaporator tubes 10 are kept particularly low.
  • throttling devices are called the inner pipe diameter D perforated shutters at one point executed and cause the operation of the continuous steam generator 2 a reduction in the throughput of the flow medium S in less heated evaporator tubes 10, whereby the Throughput of the flow medium S is adapted to the heating.
  • the throughput of the Flow medium S in the evaporator tubes 10 one or more Lines of the line system, not shown 19 with throttle devices, in particular throttle fittings, fitted.
  • Adjacent evaporator or steam generator tubes 10, 16, 17 are on their long sides in a manner not shown Welded together gas-tight via fins.
  • the respective fin width is on the hot gas side predeterminable heating profile adapted by the Position of the respective evaporator or steam generator tubes 10, 16, 17 in the continuous steam generator 2 depends.
  • the heating profile can be determined from empirical values typical heating profile or a rough estimate his.
  • there are temperature differences at the outlet the evaporator or steam generator tubes 10, 16, 17 also at greatly different heating of the evaporator or steam generator tubes 10, 16, 17 kept particularly low. To this Way, material fatigue is reliably prevented, what ensures a long service life of the continuous steam generator 2.
  • each other gas-tight welded evaporator tubes 10 when operating the Pass-through steam generator 2 is very different. therefore is the interpretation of the evaporator tubes 10 in terms of their Internal ribbing, fin connection to neighboring evaporator tubes 10 and its inner tube diameter D selected so that almost all evaporator tubes 10 despite different heating have the same outlet temperatures and sufficient Cooling of all evaporator tubes 10 for all operating states of the continuous steam generator 2 is guaranteed. Less heating of some evaporator tubes 10 during operation of the continuous steam generator 2 is by the installation of Throttle devices also taken into account.
  • the inner tube diameter D of the evaporator tubes 10 in the Combustion chamber 4 are dependent on their respective position selected in the combustion chamber 4.
  • Evaporator tubes show 10, one in the operation of the continuous steam generator 2 exposed to greater heating, a larger pipe inside diameter D on as evaporator tubes 10, which are in operation of the continuous steam generator 2 are heated less. This is compared to the case with the same inner pipe diameters achieved that the flow rate of the flow medium S in the evaporator tubes 10 with a larger tube inner diameter D increases and thus temperature differences at the outlet the evaporator tubes 10 due to different heating be reduced.
  • Evaporator tubes 10 have approximately the same specific heat absorption of the flow medium guided in the evaporator tubes 10 S during the operation of the continuous steam generator 2 and thus only slight temperature differences at their outlet.
  • the inside ribbing the evaporator tubes 10 is designed such that that a particularly reliable cooling of the evaporator tubes 10 despite different heating and flow with flow medium S in all load conditions of the once-through steam generator 2 is guaranteed.
  • the horizontal throttle cable 6 has a number of bulkhead heating surfaces trained superheater heating surfaces 22, which in hanging construction approximately perpendicular to the main flow direction 24 of the heating gas G arranged and their tubes for a flow through the flow medium S in parallel are switched.
  • the superheater heating surfaces 22 are predominant heated by convection and are on the flow medium side Evaporator tubes 10 downstream of the combustion chamber 4.
  • the vertical throttle cable 8 has a number of predominantly convective heatable convection heating surfaces 26 which come from approximately perpendicular to the main flow direction 26 of the heating gas G arranged tubes are formed. These pipes are for a flow through the flow medium S in parallel connected. There is also an economizer in the vertical throttle cable 8 28 arranged.
  • the vertical throttle cable 8 opens on the output side in another heat exchanger, for example in one Air preheater and from there via a dust filter into one Stack. The components downstream of the vertical throttle cable 8 are not shown in Figure 1.
  • the continuous steam generator 2 is horizontal Combustion chamber 4 with a particularly low overall height and thus with particularly low manufacturing and assembly costs be set up at.
  • the combustion chamber 4 of the once-through steam generator 2 a number of burners 30 for fossil Fuel B on the end wall 11 of the combustion chamber 4th are arranged at the level of the horizontal throttle cable 6.
  • the length L is so that the fossil fuel B burns out completely to achieve a particularly high efficiency and material damage to the first superheater heating surface 22 of the horizontal gas flue 6, as seen on the hot gas side, and contamination thereof, for example by the introduction of molten ash at high temperature, is particularly reliably prevented
  • Combustion chamber 4 is selected such that it exceeds the burnout length of fuel B when the continuous steam generator 2 is operating at full load.
  • the length L is the distance from the end wall 11 of the combustion chamber 4 to the inlet area 32 of the horizontal gas flue 6.
  • the burnout length of the fuel B is defined as the heating gas velocity in the horizontal direction at a specific mean heating gas temperature multiplied by the burnout time t A of the flame F des Fuel B.
  • the maximum burn-out length for the respective continuous steam generator 2 results when the respective continuous steam generator 2 is operating at full load.
  • the burn-out time t A of the flame F of the fuel B is in turn the time which, for example, a medium-sized coal dust particle takes to completely burn out at a certain average heating gas temperature ,
  • the length L (specified in m) of the combustion chamber 4 is the burnout time t as a function of the outlet temperature T BRK (specified in ° C.) of the heating gas G from the combustion chamber 4 A (specified in s) of the flame F of the fuel B and the steam flow M (specified in kg / s) of the once-through steam generator 2 at full load are selected appropriately.
  • This horizontal length L of the combustion chamber 4 is at least 80% of the height H of the combustion chamber 4. The height H is measured from the top edge of the funnel of the combustion chamber 4, marked by the line with the end points X and Y in FIG. 1, to the ceiling of the combustion chamber.
  • the quotient of the steam flow M (given in kg / s) is for a number N of evaporator tubes 10 connected in parallel. of the continuous-flow steam generator 2 at full load and the sum A (specified in m 2 ) of the inner cross-sectional area of the number N of these evaporator tubes 10, which can be acted upon in parallel with flow medium S, each having an inner tube diameter D N such that the condition is satisfied.
  • the burners 30 During operation of the continuous steam generator 2, the burners 30 fossil fuel B supplied. The flames F the Burners 30 are aligned horizontally. Because of the construction the combustion chamber 4 becomes a flow during combustion resulting heating gas G in approximately horizontal Main flow direction 24 generated. This comes through the Horizontal throttle cable 6 in the approximately aligned to the ground Vertical throttle cable 8 and leaves it in the direction of Chimneys not shown.
  • Flow medium S entering the economizer 28 arrives via the convection heating surfaces arranged in the vertical gas flue 8 26 into the inlet header system 18 of the evaporator tubes 10 of the combustion chamber 4 of the once-through steam generator 2.
  • Evaporator tubes 10 of the combustion chamber 4 of the once-through steam generator 2 finds the evaporation and if necessary partial overheating of the flow medium S instead of.
  • the resulting steam or a water-steam mixture is in the outlet collector system 20 for flow medium S collected.
  • the steam or the water-steam mixture passes from there. over the walls of the horizontal throttle cable 6 and Vertical throttle cable 8 in the superheater heating surfaces 22 of the horizontal gas cable 6.
  • the superheater heating surfaces 22 a further overheating of the steam, which then one Use, for example the drive of a steam turbine, supplied becomes.
  • the continuous steam generator 2 can be built due to its particularly low overall height and compact design with particularly low manufacturing and assembly costs. A scaffold that can be constructed with comparatively little technical effort can be provided.
  • the connecting pipes from the continuous steam generator to the steam turbine can also be designed in a particularly short manner.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Hydrogen, Water And Hydrids (AREA)
  • Fats And Perfumes (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP99964411A 1998-12-18 1999-12-06 Fossilbeheizter durchlaufdampferzeuger Expired - Lifetime EP1141625B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19858780 1998-12-18
DE19858780A DE19858780C2 (de) 1998-12-18 1998-12-18 Fossilbeheizter Durchlaufdampferzeuger
PCT/DE1999/003896 WO2000037851A1 (de) 1998-12-18 1999-12-06 Fossilbeheizter durchlaufdampferzeuger

Publications (2)

Publication Number Publication Date
EP1141625A1 EP1141625A1 (de) 2001-10-10
EP1141625B1 true EP1141625B1 (de) 2002-06-26

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EP99964411A Expired - Lifetime EP1141625B1 (de) 1998-12-18 1999-12-06 Fossilbeheizter durchlaufdampferzeuger

Country Status (12)

Country Link
US (1) US6446580B2 (ko)
EP (1) EP1141625B1 (ko)
JP (1) JP3571298B2 (ko)
KR (1) KR100685074B1 (ko)
CN (1) CN1192186C (ko)
AT (1) ATE219828T1 (ko)
CA (1) CA2355101C (ko)
DE (2) DE19858780C2 (ko)
DK (1) DK1141625T3 (ko)
ES (1) ES2179696T3 (ko)
RU (1) RU2212582C2 (ko)
WO (1) WO2000037851A1 (ko)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2501086A1 (en) * 2002-10-04 2004-04-22 Nooter/Eriksen, Inc. Once-through evaporator for a steam generator
US20050072379A1 (en) * 2003-08-15 2005-04-07 Jupiter Oxygen Corporation Device and method for boiler superheat temperature control
US7878157B2 (en) * 2004-09-23 2011-02-01 Siemens Aktiengesellschaft Fossil-fuel heated continuous steam generator
EP2065641A3 (de) * 2007-11-28 2010-06-09 Siemens Aktiengesellschaft Verfahren zum Betrieben eines Durchlaufdampferzeugers sowie Zwangdurchlaufdampferzeuger
EP2194320A1 (de) * 2008-06-12 2010-06-09 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Durchlaufdampferzeugers sowie Zwangdurchlaufdampferzeuger
EP2182278A1 (de) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Durchlaufdampferzeuger
EP2180250A1 (de) * 2008-09-09 2010-04-28 Siemens Aktiengesellschaft Durchlaufdampferzeuger
DE102009012321A1 (de) * 2009-03-09 2010-09-16 Siemens Aktiengesellschaft Durchlaufverdampfer
DE102010040208B4 (de) * 2010-09-03 2012-08-16 Siemens Aktiengesellschaft Solarthermische Durchlaufverdampfer-Heizfläche mit lokaler Querschnittsverengung an ihrem Eintritt
DE102013215456A1 (de) 2013-08-06 2015-02-12 Siemens Aktiengesellschaft Durchlaufdampferzeuger
EP3098507B1 (en) 2013-12-27 2018-09-19 Mitsubishi Hitachi Power Systems, Ltd. Heat transfer tube, boiler, and steam turbine device

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3136298A (en) * 1962-06-27 1964-06-09 Babcock & Wilcox Co Vapor generator
US3927646A (en) * 1965-04-13 1975-12-23 Babcock & Wilcox Co Vapor generator
US3527261A (en) * 1968-11-12 1970-09-08 Babcock & Wilcox Co Tube guide apparatus
DE2557427A1 (de) * 1975-12-19 1977-06-30 Kraftwerk Union Ag Schaltung einer feuerraumnase bei einem durchlaufkessel mit gasdicht verschweissten waenden in zweizugbauweise
US4290389A (en) * 1979-09-21 1981-09-22 Combustion Engineering, Inc. Once through sliding pressure steam generator
EP0349834B1 (de) * 1988-07-04 1996-04-17 Siemens Aktiengesellschaft Durchlaufdampferzeuger
EP0450072B1 (en) * 1988-12-22 1995-04-26 Miura Co., Ltd. Square multi-pipe once-through boiler
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
DE4427859A1 (de) * 1994-08-05 1995-10-26 Siemens Ag Rohr mit auf seiner Innenseite ein mehrgängiges Gewinde bildenden Rippen sowie Dampferzeuger zu seiner Verwendung
DE4431185A1 (de) * 1994-09-01 1996-03-07 Siemens Ag Durchlaufdampferzeuger
DE19645748C1 (de) * 1996-11-06 1998-03-12 Siemens Ag Verfahren zum Betreiben eines Durchlaufdampferzeugers und Durchlaufdampferzeuger zur Durchführung des Verfahrens
DE19651678A1 (de) * 1996-12-12 1998-06-25 Siemens Ag Dampferzeuger
JP4242564B2 (ja) * 1998-06-10 2009-03-25 シーメンス アクチエンゲゼルシヤフト 化石燃料用ボイラ

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DE19858780A1 (de) 2000-07-06
DE59901884D1 (de) 2002-08-01
CN1330751A (zh) 2002-01-09
US6446580B2 (en) 2002-09-10
DE19858780C2 (de) 2001-07-05
JP2002533643A (ja) 2002-10-08
EP1141625A1 (de) 2001-10-10
KR100685074B1 (ko) 2007-02-22
KR20010082364A (ko) 2001-08-29
ATE219828T1 (de) 2002-07-15
CA2355101A1 (en) 2000-06-29
WO2000037851A1 (de) 2000-06-29
US20020000208A1 (en) 2002-01-03
CA2355101C (en) 2005-07-26
JP3571298B2 (ja) 2004-09-29
DK1141625T3 (da) 2002-10-14
ES2179696T3 (es) 2003-01-16
RU2212582C2 (ru) 2003-09-20
CN1192186C (zh) 2005-03-09

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