EP1141625B1 - Fossil fuel fired continuous-flow steam generator - Google Patents

Fossil fuel fired continuous-flow steam generator 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
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Expired - Lifetime
Application number
EP99964411A
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German (de)
French (fr)
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EP1141625A1 (en
Inventor
Joachim Franke
Rudolf Kral
Eberhard Wittchow
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Siemens AG
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Siemens AG
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Publication of EP1141625A1 publication Critical patent/EP1141625A1/en
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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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  • 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)
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  • Hydrogen, Water And Hydrids (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The fossil fuel fired continuous-flow steam generator has a gas turbine combustion chamber for fossil combustibles. On the heating gas side a vertical gas extractor is mounted downstream of a horizontal gas extractor. The walls surrounding the combustion chamber are composed of vertical evaporator tubes that are welded together. During operation the temperature differences between adjacent evaporator tubes of the combustion chamber are kept as low as possible. The burners are arranged at the level of the horizontal gas extractor. For a number of evaporator tubes which can be simultaneously impinged by the flow medium the ratio of the steam generating capacity M (in kg/s) at full load and of the sum A (in m2) of the inner cross-sectional surfaces of the same evaporator tubes is less than 1350 (in kg/sm2).

Description

Die Erfindung bezieht sich auf einen Durchlaufdampferzeuger, der eine Brennkammer für fossilen Brennstoff aufweist, der heizgasseitig über einen Horizontalgaszug ein Vertikalgaszug nachgeschaltet ist, wobei die Umfassungswände der Brennkammer aus gasdicht miteinander verschweißten, vertikal angeordneten Verdampferrohren gebildet sind.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.

Ein gattungsgemäßer Dampferzeuger ist in US-A-3 527 261 beschrieben.A generic steam generator is described in US-A-3 527 261.

Bei einer Kraftwerksanlage mit einem Dampferzeuger wird der Energiegehalt eines Brennstoffs zur Verdampfung von einem Strömungsmedium im Dampferzeuger genutzt. Dabei wird das Strömungsmedium üblicherweise in einem Verdampferkreislauf geführt. Der durch den Dampferzeuger bereitgestellte Dampf wiederum kann beispielsweise für den Antrieb einer Dampfturbine und/oder für einen angeschlossenen externen Prozeß vorgesehen sein. Treibt der Dampf eine Dampfturbine an, so wird über die Turbinenwelle der Dampfturbine üblicherweise ein Generator oder eine Arbeitsmaschine betrieben. Im Falle eines Generators kann der durch den Generator erzeugte Strom zur Einspeisung in ein Verbund- und/oder Inselnetz vorgesehen sein.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.

Der Dampferzeuger kann dabei als Durchlaufdampferzeuger ausgebildet sein. Ein Durchlaufdampferzeuger ist aus dem Aufsatz "Verdampferkonzepte für Benson-Dampferzeuger" von J. Franke, W. Köhler und E. Wittchow, veröffentlicht in VGB Kraftwerkstechnik 73 (1993), Heft 4, S. 352-360, bekannt. Bei einem Durchlaufdampferzeuger führt die Beheizung von als Verdampferrohren vorgesehenen Dampferzeugerrohren zu einer Verdampfung des Strömungsmediums in den Dampferzeugerrohren in einem einmaligen Durchlauf.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.

Durchlaufdampferzeuger werden üblicherweise mit einer Brennkammer in vertikaler Bauweise ausgeführt. Dies bedeutet, daß die Brennkammer für eine Durchströmung des beheizenden Mediums oder Heizgases in annähernd vertikaler Richtung ausgelegt ist. Heizgasseitig kann der Brennkammer dabei ein Horizontalgaszug nachgeschaltet sein, wobei beim Übergang von der Brennkammer in den Horizontalgaszug eine Umlenkung des Heizgasstroms in eine annähernd horizontale Strömungsrichtung erfolgt. Derartige Brennkammern erfordern jedoch im allgemeinen aufgrund der temperaturbedingten Längenänderungen der Brennkammer ein Gerüst, an dem die Brennkammer aufgehängt wird. Dies bedingt einen erheblichen technischen Aufwand bei der Herstellung und Montage des Durchlaufdampferzeugers, der um so größer ist, je größer die Bauhöhe des Durchlaufdampferzeugers ist. Dies ist insbesondere bei Durchlaufdampferzeugern der Fall, die für einen Dampfstrom von mehr als 80 kg/s bei Vollast ausgelegt sind.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. However, 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.

Ein Durchlaufdampferzeuger unterliegt keiner Druckbegrenzung, so daß Frischdampfdrücke weit über dem kritischen Druck von Wasser (pkri = 221 bar) - wo es nur noch einen geringen Dichteunterschied gibt zwischen flüssigkeitsähnlichem und dampfähnlichem Medium - möglich sind. Ein hoher Frischdampfdruck begünstigt einen hohen thermischen Wirkungsgrad und somit niedrige CO2-Emissionen eines fossilbeheizten Kraftwerks, das beispielsweise mit Steinkohle oder auch mit Braunkohle als Brennstoff befeuert sein kann.A continuous steam generator is not subject to any pressure limitation, so that live steam pressures far above the critical pressure of water (p kri = 221 bar) - where there is only a slight difference in density between liquid-like and vapor-like medium - are possible. 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.

Ein besonderes Problem stellt die Auslegung der Umfassungswand des Gaszuges oder Brennkammer des Durchlaufdampferzeugers im Hinblick auf die dort auftretenden Rohrwand- oder Materialtemperaturen dar. Im unterkritischen Druckbereich bis etwa 200 bar wird die Temperatur der Umfassungswand der Brennkammer im wesentlichen von der Höhe der Sättigungstemperatur des Wassers bestimmt, wenn eine Benetzung der Innenoberfläche der Verdampferrohre sichergestellt werden kann. Dies wird beispielsweise durch die Verwendung von Verdampferrohren erzielt, die auf ihrer Innenseite eine Oberflächenstruktur aufweisen. Dazu kommen insbesondere innenberippte Verdampferrohre in Betracht, deren Einsatz in einem Durchlaufdampferzeuger beispielsweise aus dem oben zitierten Aufsatz bekannt ist. Diese sogenannten Rippenrohre, d.h. Rohre mit einer berippten Innenoberfläche, haben einen besonders guten Wärmeübergang von der Rohrinnenwand zum Strömungsmedium.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. In addition, there are in particular 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.

Erfahrungsgemäß läßt es sich nicht vermeiden, daß die Umfassungswand der Brennkammer unterschiedlich beheizt wird. Aufgrund der unterschiedlichen Beheizung der Verdampferrohre können die Austrittstemperaturen des Strömungsmediums aus mehrbeheizten Verdampferrohren daher bei Durchlaufdampferzeugern im allgemeinen höher als bei normal- oder minderbeheizten Verdampferrohren liegen. Dadurch können Temperaturdifferenzen zwischen benachbarten Verdampferrohren entstehen, die zu Wärmespannungen führen, welche die Lebensdauer des Durchlaufdampferzeugers herabsetzen oder sogar Rohrreißer verursachen könnenExperience has shown that the surrounding wall cannot be avoided the combustion chamber is heated differently. by virtue of the different heating of the evaporator tubes can determine the outlet temperatures of the flow medium multi-heated evaporator tubes therefore in continuous steam generators generally higher than those with normal or low heating Evaporator tubes are lying. This can cause temperature differences between adjacent evaporator tubes that arise lead to thermal stresses that affect the life of the once-through steam generator lower it or even cause pipe rips can

Der Erfindung liegt daher die Aufgabe zugrunde, einen fossilbeheizten Durchlaufdampferzeuger der oben genannten Art anzugeben, der einen besonders geringen Herstellungs- und Montageaufwand erfordert, und bei dessen Betrieb außerdem Temperaturunterschiede zwischen benachbarten Verdampferrohren der Brennkammer besonders gering gehalten sind.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.

Diese Aufgabe wird erfindungsgemäß gelöst, indem der Durchlaufdampferzeuger eine Brennkammer mit einer Anzahl von in der Höhe des Horizontalgaszugs angeordneten Brennern aufweist und derart ausgelegt ist, daß für jeweils eine Anzahl von parallel mit Strömungsmedium beaufschlagbaren Verdampferrohren der aus dem Dampfstrom M (angegeben in kg/s) bei Vollast und der Summe der Innenquerschnittsflächen A (angegeben in m2) dieser parallel mit Strömungsmedium beaufschlagbaren Verdampferrohre gebildete Quotient kleiner ist als 1350 (angegeben in kg/sm2). This object is achieved according to the invention in that 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 ).

Die Erfindung geht von der Überlegung aus, daß ein mit besonders geringem Herstellungs- und Montageaufwand erstellbarer Durchlaufdampferzeuger eine mit einfachen Mitteln ausführbare Aufhängekonstruktion aufweisen sollte. Ein mit vergleichsweise geringem technischem Aufwand zu erstellendes Gerüst für die Aufhängung der Brennkammer kann dabei einhergehen mit einer besonders geringen Bauhöhe des Durchlaufdampferzeugers. Eine besonders geringe Bauhöhe des Durchlaufdampferzeugers ist erzielbar, indem die Brennkammer in horizontaler Bauweise ausgeführt ist. Hierzu sind die Brenner in der Höhe des Horizontalgaszugs in der Brennkammerwand angeordnet. Somit strömt beim Betrieb des Durchlaufdampferzeugers das Heizgas in annähernd horizontaler Hauptströmungsrichtung durch die Brennkammer.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. For this purpose, the burners are at the level of the horizontal gas flue arranged in the combustion chamber wall. Thus flows when operating the once-through steam generator, the heating gas in approximately horizontal main flow direction through the combustion chamber.

Bei einer horizontalen Brennkammer wird nun aber beim Betrieb des Durchlaufdampferzeugers der heizgasseitig gesehen hintere Bereich der Brennkammer vergleichsweise geringer als der heizgasseitig gesehen vordere Bereich der Brennkammer beheizt. Außerdem wird beispielsweise ein Verdampferrohr in Brennernähe mehrbeheizt als ein in einer Brennkammerecke angeordnetes Verdampferrohr. Dabei kann im Extremfall im vorderen Bereich der Brennkammer die Beheizung etwa dreimal größer sein als im hinteren Bereich. Bei den bisher üblichen Massenstromdichten in den Verdampferrohren- angegeben in kg/m2s und bezogen auf 100% Dampfleistung (Vollast) - von 2000 kg/m2s geht der Massendurchsatz in einem mehrbeheizten Rohr zurück und steigt in einem minderbeheizten Rohr an, jeweils bezogen auf den Mittelwert des Massendurchsatzes aller Rohre. Dieses Verhalten wird durch den relativ hohen Anteil des Reibungsdruckverlustes am gesamten Druckabfall der Verdampferrohre verursacht. Außerdem sind die relativen Längenunterschiede der Verdampferrohre aufgrund der besonders niedrigen Höhe der Brennkammer wesentlich größer als bei einer vertikalen Brennkammer. Dies verstärkt zusätzlich die Unterschiede in der Beheizung und im Reibungsdruckverlust der einzelnen Verdampferrohre. Um dennoch annähernd gleiche Temperaturen zwischen benachbarten Verdampferrohren sicherzustellen, sollte der Durchlaufdampferzeuger derart ausgelegt sein, daß sich in einem vergleichsweise mehrbeheizten Verdampferrohr selbsttätig ein höherer Durchsatz des Strömungsmediums einstellt als in einem vergleichsweise minderbeheizten Verdampferrohr.Dies ist im allgemeinen dann der Fall, wenn der geodätische Druckabfall ΔpG (angegeben in bar) eines Verdampferrohres mit mittlerer Beheizung ein Mehrfaches seines Reibungsdruckverlustes ΔpR (angegeben in bar) beträgt. Die Bedingung für einen Durchsatzanstieg in einem vergleichsweise mehrbeheizten Verdampferrohr bei konstantem Massenstrom lautet:

Figure 00050001
wobei ΔpB (angegeben in bar) eine Änderung des Beschleunigungsdruckabfalls, ΔQ (angegeben in kJ/s) eine Änderung der Beheizung, M (angegenben in kg/s) der Massenstrom und K (angegeben in (bar s)/kJ) eine Konstante ist. Die in dieser Ungleichung formulierte Bedingung gibt an, daß bei konstantem Massenstrom der Gesamtdruckverlusts Δ(ΔpG + ΔpR + ΔpB) (angegeben in bar) bei einer Mehrbeheizung ΔQ abnehmen, d.h. mathematisch negativ werden muß. Wenn also in einer Anzahl von Verdampferrohren der gleiche Gesamtdruckverlust herrscht, dann muß in einem mehrbeheizten Verdampferrohr im Vergleich zu einem minderbeheizten Verdampferrohr entsprechend der obengenannten Ungleichung der Durchsatz des Strömungsmediums steigen.In the case of a horizontal combustion chamber, however, the rear region of the combustion chamber, as seen on the hot gas side, 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. In addition, for example, an evaporator tube near the burner is heated more than an evaporator tube arranged in a corner of the combustion chamber. In extreme cases, the heating in the front area of the combustion chamber can be about three times greater than in the rear area. In the usual mass flow density in the Verdampferrohren- given in kg / m 2 s, and based on 100% steam power (full load) - 2000 kg / m 2 s the mass flow rate is in a multi-tube heated and rises in a less heated tube, in each case based on the average mass flow of all pipes. This behavior is caused by the relatively high proportion of the friction pressure loss in the total pressure drop of the evaporator tubes. In addition, due to the particularly low height of the combustion chamber, the relative differences in length of the evaporator tubes are significantly greater than in the case of a vertical combustion chamber. This additionally reinforces the differences in heating and in the loss of friction pressure of the individual evaporator tubes. In order to ensure that the temperatures between adjacent evaporator tubes are still approximately the same, 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 Δp G (specified in bar) of an evaporator tube with medium heating is a multiple of its frictional pressure loss Δp R (specified in bar). The condition for an increase in throughput in a comparatively more heated evaporator tube at constant mass flow is:
Figure 00050001
where Δp B (given in bar) is a change in the acceleration pressure drop, ΔQ (given in kJ / s) a change in heating, M (given in kg / s) the mass flow and 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 Δ (Δp G + Δp R + Δp B ) (given in bar) decreases in the case of additional heating ΔQ, ie must become mathematically negative. If, therefore, the same total pressure loss prevails in a number of evaporator tubes, then 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.

Umfangreiche Rechnungen haben nun überraschenderweise ergeben, daß die in der Ungleichung formulierte Bedingung für Durchlaufdampferzeuger mit horizontaler Brennkammer erfüllt ist, wenn für eine Anzahl von parallel geschalteten Verdampferrohren der Quotient aus dem Dampfstrom M (angegeben in kg/s) des Durchlaufdampferzeugers bei Vollast und der aus der Summe der Innenquerschnittsflächen A (angegeben in m2) dieser parallel geschalteten Verdampferrohre nicht größer ist als 1350 (angegeben in kg/sm2). Also mathematisch formuliert: M A < 1350. . Comprehensive calculations have now surprisingly shown that the condition formulated in the inequality for continuous steam generators with a horizontal combustion chamber is met if the quotient of the steam flow M (specified in kg / s) of the continuous steam generator at full load and off for a number of evaporator tubes connected in parallel the sum of the internal cross-sectional areas A (specified in m 2 ) of these evaporator tubes connected in parallel is not greater than 1350 (specified in kg / sm 2 ). So formulated mathematically: M A <1350..

Dabei wird der Dampfstrom M bei Vollast des Durchlaufdampferzeugers auch als zulässige Dampferzeugung oder als Boiler maximum continuous rating (BMCR) bezeichnet, und die jeweilige Innenquerschnittsfläche eines Verdampferrohrs ist auf einen horizontalen Schnitt bezogen.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.

Vorteilhafterweise ist jeweils einer Anzahl von parallel geschalteten Verdampferrohren der Brennkammer ein gemeinsames Eintrittssammler-System vorgeschaltet und ein gemeinsames Austrittssammler-System für Strömungsmedium nachgeschaltet. Ein in dieser Ausgestaltung ausgeführter Durchlaufdampferzeuger ermöglicht nämlich einen zuverlässigen Druckausgleich zwischen einer Anzahl von parallel geschalteten Verdampferrohren, so daß jeweils alle parallel geschalteten Verdampferrohre den gleichen Gesamtdruckverlust aufweisen. Dies bedeutet, daß bei einem mehrbeheizten Verdampferrohr im Vergleich zu einem minderbeheizten Verdampferrohr entsprechend der obengenannten Ungleichung der Durchsatz steigen muß.Advantageously, 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.

Die Verdampferrohre der Stirnwand der Brennkammer sind vorteilhafterweise den Verdampferrohren der Umfassungswände, die die Seitenwände der Brennkammer bilden, strömungsmediumsseitig vorgeschaltet. Dadurch ist eine besonders günstige Kühlung der stark beheizten Stirnwand der Brennkammer gewährleistet.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.

In einer weiteren vorteilhaften Ausgestaltung der Erfindung ist der Rohrinnendurchmesser einer Anzahl der Verdampferrohre der Brennkammer abhängig von der jeweiligen Position der Verdampferrohre in der Brennkammer gewählt. Auf diese Weise sind die Verdampferrohre in der Brennkammer an ein heizgasseitig vorgebbares Beheizungsprofil anpaßbar. Mit dem hierdurch bewirkten Einfluß auf die Durchströmung der Verdampferrohre sind besonders zuverlässig Temperaturunterschiede am Austritt der Verdampferrohre der Brennkammer gering gehalten.In 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.

Für eine besonders gute Wärmeübertragung von der Wärme der Brennkammer auf das in den Verdampferrohren geführte Strömungsmedium weist vorteilhafterweise eine Anzahl der Verdampferrohre auf ihrer Innenseite jeweils ein mehrgängiges Gewinde bildende Rippen auf. Dabei ist vorteilhafterweise ein Steigungswinkel α zwischen einer zur Rohrachse senkrechten Ebene und den Flanken der auf der Rohrinnenseite angeordneten Rippen kleiner als 60°, vorzugsweise kleiner als 55°.For a particularly good heat transfer from the heat of the Combustion chamber on the flow medium in the evaporator tubes advantageously has a number of evaporator tubes a multi-start thread on the inside forming ribs. This is advantageously a Pitch angle α 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 °.

In einem beheizten, als Verdampferrohr ohne Innenberippung, einem sogenannten Glattrohr, ausgeführten Verdampferrohr kann nämlich von einem bestimmten Dampfgehalt an die für einen besonders guten Wärmeübergang erforderliche Benetzung der Rohrwand nicht mehr aufrechterhalten werden. Bei fehlender Benetzung kann eine stellenweise trockene Rohrwand vorliegen. Der Übergang zu einer derartigen trockenen Rohrwand führt zu einer sogenannten Wärmeübergangskrise mit verschlechtertem Wärmeübergangsverhalten, so daß im allgemeinen die Rohrwandtemperaturen an dieser Stelle besonders stark ansteigen. In einem innenberippten Verdampferrohr tritt aber nun im Vergleich zu einem Glattrohr diese Krise des Wärmeübergangs erst bei einem Dampfmassengehalt > 0,9, also kurz vor dem Ende der Verdampfung, auf. Das ist auf den Drall zurückzuführen, den die Strömung durch die spiralförmigen Rippen erfährt. Aufgrund der unterschiedlichen Zentrifugalkraft wird der Wasservom Dampfanteil separiert und an die Rohrwand transportiert. Dadurch wird die Benetzung der Rohrwand bis zu hohen Dampfgehalten aufrechterhalten, so daß am Ort der Wärmeübergangskrise bereits hohe Strömungsgeschwindigkeiten vorliegen. Das bewirkt trotz Wärmeübergangskrise einen relativ guten Wärmeübergang und als Folge niedrige Rohrwandtemperaturen.In a heated, as an evaporator tube without internal fins, 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. In one internally finned evaporator tube now occurs in comparison 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. This is due to the twist that experiences the flow through the spiral ribs. by virtue of the difference in centrifugal force becomes water Steam component separated and transported to the pipe wall. As a result, the wetting of the pipe wall up to high steam contents maintained so that at the site of the heat transfer crisis there are already high flow velocities. The causes a relatively good heat transfer despite the heat transfer crisis and as a result, low tube wall temperatures.

Eine Anzahl der Verdampferrohre der Brennkammer weist vorteilhafterweise Mittel zum Reduzieren des Durchflusses des Strömungsmediums auf. Dabei erweist es sich als besonders günstig, wenn die Mittel als Drosseleinrichtungen ausgebildet sind. Drosseleinrichtungen können beispielweise Einbauten in die Verdampferrohre sein, die an einer Stelle im Inneren des jeweiligen Verdampferrohrs den Rohrinnendurchmesser verkleinern. Dabei erweisen sich auch Mittel zum Reduzieren des Durchflusses in einem mehrere parallele Leitungen umfassenden Leitungssystem als vorteilhaft, durch das den Verdampferrohren der Brennkammer Strömungsmedium zuführbar ist. Dabei kann das Leitungssystem auch einem Eintrittssammler-System von parallel mit Strömungsmedium beaufschlagbaren Verdampferrohren vorgeschaltet sein. In einer Leitung oder in mehreren Leitungen des Leitungssystems können dabei beispielweise Drosselarmaturen vorgesehen sein. Mit solchen Mitteln zur Reduzierung des Durchflusses des Strömungsmediums durch die Verdampferrohre läßt sich eine Anpassung des Durchsatzes des Strömungsmediums durch einzelne Verdampferrohre an deren jeweilige Beheizung in der Brennkammer herbeiführen. Dadurch sind zusätzlich Temperaturunterschiede des Strömungsmediums am Austritt der Verdampferrohre besonders zuverlässig besonders gering gehalten.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. With such means of reduction 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.

Die Seitenwände des Horizontalgaszugs und/oder des Vertikalgaszugs sind vorteilhafterweise aus gasdicht miteinander verschweißten, vertikal angeordneten, jeweils parallel mit Strömungsmedium beaufschlagbaren Dampferzeugerrohren gebildet.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.

Benachbarte Verdampfer- bzw. Dampferzeugerrohre sind an ihren Längsseiten vorteilhafterweise über Metallbänder, sogenannte Flossen, gasdicht miteinander verschweißt. Diese Flossen können im Herstellungsverfahren der Rohre bereits fest mit den Rohren verbunden sein und mit diesen eine Einheit bilden. Diese aus einem Rohr und Flossen gebildete Einheit wird auch als Flossenrohr bezeichnet. Die Flossenbreite beeinflußt den Wärmeeintrag in die Verdampfer- bzw. Dampferzeugerrohre. Daher ist die Flossenbreite vorzugsweise abhängig von der Position der jeweiligen Verdampfer- bzw. Dampferzeugerrohre im Durchlaufdampferzeuger an ein heizgasseitig vorgebbares Beheizungsprofil angepaßt. Als Beheizungsprofil kann dabei ein aus Erfahrungswerten ermitteltes typisches Beheizungsprofil oder auch eine grobe Abschätzung, wie beispielsweise ein stufenförmiges Beheizungsprofil, vorgegeben sein. Durch die geeignet gewählten Flossenbreiten ist auch bei stark unterschiedlicher Beheizung verschiedener Verdampfer- bzw. Dampferzeugerrohre ein Wärmeeintrag in alle Verdampfer- bzw. Dampferzeugerrohre derart erreichbar, daß Temperaturunterschiede am Austritt der Verdampfer- bzw. Dampferzeugerrohre besonders gering gehalten sind. Auf diese Weise sind vorzeitige Materialermüdungen zuverlässig verhindert. Dadurch weist der Durchlaufdampferzeuger eine besonders lange Lebensdauer auf.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. By 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.

In dem Horizontalgaszug sind vorteilhafterweise eine Anzahl von Überhitzerheizflächen angeordnet, die annähernd senkrecht zur Hauptströmungsrichtung des Heizgases angeordnet und deren Rohre für eine Durchströmung des Strömungsmediums parallel geschaltet sind. Diese in hängender Bauweise angeordneten, auch als Schottheizflächen bezeichneten, Überhitzerheizflächen werden überwiegend konvektiv beheizt und sind strömungsmediumsseitig den Verdampferrohren der Brennkammer nachgeschaltet. Hierdurch ist eine besonders günstige Ausnutzung der Heizgaswärme gewährleistet.There are advantageously a number in the horizontal throttle cable arranged by superheater heating surfaces that are approximately vertical arranged to the main flow direction of the heating gas and their Pipes for a flow of the flow medium in parallel are switched. These are arranged in a hanging construction, also referred to as bulkhead heating surfaces, superheater heating surfaces are predominantly heated by convection and are on the flow medium side downstream of the evaporator tubes of the combustion chamber. This is a particularly favorable exploitation the heating gas heat guaranteed.

Vorteilhafterweise weist der Vertikalgaszug eine Anzahl von Konvektionsheizflächen auf, die aus annähernd senkrecht zur Hauptströmungsrichtung des Heizgases angeordneten Rohren gebildet sind. Diese Rohre einer Konvektionsheizfläche sind für eine Durchströmung des Strömungsmediums parallel geschaltet. Auch diese Konvektionsheizflächen werden überwiegend konvektiv beheizt.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.

Um weiterhin eine besonders vollständige Ausnutzung der Wärme des Heizgases zu gewährleisten, weist der Vertikalgaszug vorteilhafterweise einen Economizer auf. To continue to make full use of the heat To ensure the heating gas, the vertical throttle cable advantageously has an economizer.

Vorteilhafterweise sind die Brenner an der Stirnwand der Brennkammer angeordnet, also an derjenigen Seitenwand der Brennkammer, die der Abströmöffnung zum Horizontalgaszug gegenüberliegt. Ein derartig ausgebildeter Durchlaufdampferzeuger ist auf besonders einfache Weise an die Ausbrandlänge des Brennstoffs anpaßbar. Unter Ausbrandlänge des Brennstoffs ist dabei die Heizgasgeschwindigkeit in horizontaler Richtung bei einer bestimmten mittleren Heizgastemperatur multipliziert mit der Ausbrandzeit tA der Flamme des Brennstoffs zu verstehen. Die für den jeweiligen Durchlaufdampferzeuger maximale Ausbrandlänge ergibt sich dabei bei dem Dampfstrom M bei Vollast des Durchlaufdampferzeugers, dem sogenannten Vollastbetrieb. Die Ausbrandzeit tA der Flamme des Brennstoffs wiederum ist die Zeit, die beispielsweise ein Kohlenstaubkorn mittlerer Größe benötigt, um bei einer bestimmten mittleren Heizgastemperatur vollständig auszubrennen.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.

Um Materialschäden und eine unerwünschte Verschmutzung des Horizontalgaszuges, beispielsweise aufgrund des Eintrags von schmelzflüssiger Asche einer hohen Temperatur, besonders gering zu halten, ist die durch den Abstand von der Stirnwand zum Eintrittsbereich des Horizontalgaszuges definierte Länge der Brennkammer vorteilhafterweise mindestens gleich der Ausbrandlänge des Brennstoffs beim Vollastbetrieb des Durchlaufdampferzeugers. Diese horizontale Länge der Brennkammer wird im allgemeinen mindestens 80 % der Höhe der Brennkammer betragen, gemessen von der Trichteroberkante bis zur Brennkammerdecke.To material damage and unwanted pollution of the Horizontal throttle cable, for example due to the entry of molten ash of a high temperature, particularly low to hold is by the distance from the front wall length defined to the entry area of the horizontal throttle cable 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.

Die Länge L (angegeben in m) der Brennkammer ist für eine besonders günstige Ausnutzung der Verbrennungswärme des fossilen Brennstoffs vorteilhafterweise als Funktion des Dampfstroms M (angegeben in kg/s) des Durchlaufdampferzeugers bei Vollast, der Ausbrandzeit tA (angegeben in s) der Flamme des fossilen Brennstoffs und der Austrittstemperatur TBRK (angegeben in °C) des Heizgases aus der Brennkammer gewählt. Dabei gilt bei gegebenem Dampfstrom M des Durchlaufdampferzeugers bei Vollast für die Länge L der Brennkammer näherungsweise der größere Wert der beiden Funktionen (1) und (2): L (M, tA) = (C1 + C2 · W) · tA und L (M, TBRK) = (C3 · TBRK + C4)W + C5(TBRK)2 + C6 · TBRK + C7 mit C1 = 8 m/s und C2 = 0,0057 m/kg und C3 = -1,905 · 10-4 (m · s)/(kg°C) und C4 = 0,286 (s · m)/kg und C5 = 3 · 10-4 m/ (°C)2 und C6 = -0,842 m/°C und C7 = 603,41 m. 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. For a given steam flow M of the continuous steam generator at full load, the length L of the combustion chamber approximately applies to the larger value of the two functions (1) and (2): L (M, t A ) = (C 1 + C 2 · W) · t A and L (M, T BRK ) = (C 3 · T BRK + C 4 ) W + C 5 (T BRK ) 2 + C 6 · T BRK + C 7 With C 1 = 8 m / s and C 2 = 0.0057 m / kg and C 3 = -1.905.10 -4 (ms) / (kg ° C) and C 4 = 0.286 (s · m) / kg and C 5 = 3 · 10 -4 m / (° C) 2 and C 6 = -0.842 m / ° C and C 7 = 603.41 m.

Unter "näherungsweise" ist hierbei eine zulässige Abweichung vom durch die jeweilige Funktion definierten Wert um +20%/-10% zu verstehen.Under "approximate" is a permissible deviation from the value defined by the respective function by +20% / - 10% to understand.

Die mit der Erfindung erzielten Vorteile bestehen insbesondere darin, daß durch die geeignete Wahl des Verhältnisses zwischen des Dampfstromes des Durchlaufdampferzeugers bei Vollast für eine Anzahl von parallel geschalteten Verdampferrohren und der Innenquerschnittsflächen dieser Verdampferrohre eine besonders gute Anpassung des Durchsatzes des Strömungsmediums durch die Verdampferrohre an die Beheizung und dadurch nahezu gleiche Temperaturen am Austritt der Verdampferrohre gewährleistet sind. Die durch Temperaturdifferenzen zwischen benachbarten Verdampferrohren verursachten Wärmespannungen in der Umfassungswand der Brennkammer bleiben dabei beim Betrieb des Durchlaufdampferzeugers weit unter den Werten, bei denen beispielsweise die Gefahr von Rohrreißern gegeben ist. Damit ist der Einsatz einer horizontalen Brennkammer in einem Durchlaufdampferzeuger auch mit vergleichsweise langer Lebensdauer möglich. Durch die Auslegung der Brennkammer für eine annähernd horizontale Hauptströmungsrichtung des Heizgases ist außerdem eine besonders kompakte Bauweise des Durchlaufdampferzeugers gegeben. Dies ermöglicht bei Einbindung des Durchlaufdampferzeugers in ein Kraftwerk mit einer Dampfturbine auch besonders kurze Verbindungsrohre von dem Durchlaufdampferzeuger zu der Dampfturbine.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. By interpreting the Combustion chamber for an almost horizontal main flow direction 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.

Ein Ausführungsbeispiel der Erfindung wird anhand einer Zeichnung näher erläutert. Darin zeigen:

FIG 1
schematisch einen fossilbeheizten Durchlaufdampferzeuger in Zweizugbauart in Seitenansicht und
FIG 2
schematisch einen Längsschnitt durch ein einzelnes Verdampferrohr und
FIG 3
ein Koordinatensystem mit den Kurven K1 bis K6.
An embodiment of the invention is explained in more detail with reference to a drawing. In it show:
FIG. 1
schematically a fossil-heated continuous steam generator in two-pass design in side view and
FIG 2
schematically shows a longitudinal section through a single evaporator tube and
FIG 3
a coordinate system with the curves K 1 to K 6 .

Einander entsprechende Teile sind in allen Figuren mit den gleichen Bezugszeichen versehen.Corresponding parts are in all figures with the provided with the same reference numerals.

Der Durchlaufdampferzeuger 2 gemäß Figur 1 ist einer nicht näher dargestellten Kraftwerksanlage zugeordnet, die auch eine Dampfturbinenanlage umfaßt. Dabei ist der Durchlaufdampferzeuger für einen Dampfstrom bei Vollast von mindestens 80 kg/s ausgelegt. Der im Durchlaufdampferzeuger 2 erzeugte Dampf wird dabei zum Antrieb der Dampfturbine genutzt, die ihrerseits wiederum einen Generator zur Stromerzeugung antreibt. Der durch den Generator erzeugte Strom ist dabei zur Einspeisung in ein Verbund- oder ein Inselnetz vorgesehen.The continuous steam generator 2 according to FIG. 1 is not one assigned power plant, which also comprises a steam turbine plant. Here is 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.

Der fossilbeheizte Durchlaufdampferzeuger 2 umfaßt eine in horizontaler Bauweise ausgeführte Brennkammer 4, der heizgasseitig über einen Horizontalgaszug 6 ein Vertikalgaszug 8 nachgeschaltet ist. Die Umfassungswände 9 der Brennkammer 4 sind aus gasdicht miteinander verschweißten, vertikal angeordneten Verdampferrohren 10 gebildet, von denen eine Anzahl N parallel mit Strömungsmedium S beaufschlagbar ist. Dabei ist eine Umfassungswand 9 der Brennkammer 4 die Stirnwand 11. Zusätzlich können auch die Seitenwände 12 des Horizontalgaszugs 6 bzw. 14 des Vertikalgaszugs 8 aus gasdicht miteinander verschweißten, vertikal angeordneten Dampferzeugerrohren 16 bzw. 17 gebildet sein. In diesem Fall sind die Dampferzeugerrohre 16 bzw. 17 jeweils parallel mit Strömungsmedium S beaufschlagbar.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. there is a peripheral wall 9 of the combustion chamber 4, the end wall 11. In addition, 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.

Einer Anzahl der Verdampferrohre 10 der Brennkammer 4 ist strömungsmediumsseitig ein Eintrittssammler-System 18 für Strömungsmedium S vorgeschaltet und ein Austrittssammler-System 20 nachgeschaltet. Das Eintrittssammler-System 18 umfaßt dabei eine Anzahl von parallelen Eintritsssammlern. Dabei ist zum Zuführen von Strömungsmedium S in das Eintrittssammler-System 18 der Verdampferrohre 10 ein Leitungssystem 19 vorgesehen. Das Leitungssystems 19 umfaßt mehrere parallel geschaltete Leitungen, die jeweils mit einem der Eintrittssammler des Eintrittssammler-Systems 18 verbunden sind.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.

Die Verdampferrohre 10 weisen - wie in Figur 2 dargestellt - einen Rohrinnendurchmesser D und auf ihrer Innenseite Rippen 40 auf, die eine Art mehrgängiges Gewinde bilden und eine Rippenhöhe R haben. Dabei ist der Steigungswinkel α zwischen einer zur Rohrachse senkrechten Ebene 42 und den Flanken 44 der auf der Rohrinnenseite angeordneten Rippen 40 kleiner als 55°. Dadurch werden ein besonders hoher Wärmeübergang von den Innenwänden der Verdampferrohre 10 an das in den Verdampferrohren 10 geführte Strömungsmedium S und gleichzeitig besonders niedrige Temperaturen der Rohrwand erreicht.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 α 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.

Der Rohrinnendurchmesser D der Verdampferrohre 10 der Brennkammer 4 ist abhängig von der jeweiligen Position der Verdampferrohre 10 in der Brennkammer 4 gewählt. Auf diese Weise ist der Durchlaufdampferzeuger 2 an die unterschiedlich starke Beheizung der Verdampferrohre 10 angepaßt. Diese Auslegung der Verdampferrohre 10 der Brennkammer 4 gewährleistet besonders zuverlässig, daß Temperaturunterschiede am Austritt der Verdampferrohre 10 besonders gering gehalten sind.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.

Als Mittel zum Reduzieren des Durchflusses des Strömungsmediums S sind ein Teil der Verdampferrohre 10 mit Drosseleinrichtungen ausgestattet, die in der Zeichnung nicht näher dargestellt sind. Die Drosseleinrichtungen sind als den Rohrinnendurchmesser D an einer Stelle verkleinernde Lochblenden ausgeführt und bewirken beim Betrieb des Durchlaufdampferzeugers 2 eine Reduzierung des Durchsatzes des Strömungsmediums S in minderbeheizten Verdamerrohren 10, wodurch der Durchsatz des Strömungsmediums S der Beheizung angepaßt wird. Weiterhin sind als Mittel zum Reduzieren des Durchsatzes des Strömungsmediums S in den Verdampferrohren 10 eine oder mehrere nicht näher dargestellte Leitungen des Leitungssystems 19 mit Drosseleinrichtungen, insbesondere Drosselarmaturen, ausgestattet.As a means of reducing the flow of the flow medium S are part of the evaporator tubes 10 with throttling devices equipped, which are not shown in the drawing are shown. The 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. Furthermore, as a means of reducing 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.

Benachbarte Verdampfer- bzw. Dampferzeugerrohre 10, 16, 17 sind in nicht näher dargestellter Weise an ihren Längsseiten über Flossen gasdicht miteinander verschweißt. Durch eine geeignete Wahl der Flossenbreite kann nämlich die Beheizung der Verdampfer- bzw. Dampferzeugerrohre 10, 16, 17 beeinflußt werden. Daher ist die jeweilige Flossenbreite an ein heizgasseitig vorgebbares Beheizungsprofil angepaßt, das von der Position der jeweiligen Verdampfer- bzw. Dampferzeugerrohre 10, 16, 17 im Durchlaufdampferzeuger 2 abhängt. Das Beheizungsprofil kann dabei ein aus Erfahrungswerten ermitteltes typisches Beheizungsprofil oder auch eine grobe Abschätzung sein. Dadurch sind Temperaturunterschiede am Austritt der Verdampfer- bzw. Dampferzeugerrohre 10, 16, 17 auch bei stark unterschiedlicher Beheizung der Verdampfer- bzw. Dampferzeugerrohre 10, 16, 17 besonders gering gehalten. Auf diese Weise sind Materialermüdungen zuverlässig verhindert, was eine lange Lebensdauer des Durchlaufdampferzeugers 2 gewährleistet. 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. By a suitable one Choice of fin width can namely the heating of the Evaporator or steam generator tubes 10, 16, 17 influenced become. Therefore, 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. As a result, 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.

Bei der Berohrung der horizontalen Brennkammer 4 ist zu berücksichtigen, daß die Beheizung der einzelnen, miteinander gasdicht verschweißten Verdampferrohre 10 beim Betrieb des Durchlaufdampferzeugers 2 sehr unterschiedlich ist. Deswegen wird die Auslegung der Verdampferrohre 10 hinsichtlich ihrer Innenberippung, Flossenverbindung zu benachbarten Verdampferrohren 10 und ihres Rohrinnendurchmessers D so gewählt, daß alle Verdampferrohre 10 trotz unterschiedlicher Beheizung annähernd gleiche Austrittstemperaturen aufweisen und eine ausreichende Kühlung aller Verdampferrohre 10 für alle Betriebszustände des Durchlaufdampferzeugers 2 gewährleistet ist. Eine Minderbeheizung einiger Verdampferrohre 10 beim Betrieb des Durchlaufdampferzeugers 2 wird dabei durch den Einbau von Drosseleinrichtungen zusätzlich berücksichtigt.When piping the horizontal combustion chamber 4, it must be taken into account that heating the individual, 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.

Die Rohrinnendurchmesser D der Verdampferrohre 10 in der Brennkammer 4 sind in Abhängigkeit von ihrer jeweiligen Position in der Brennkammer 4 gewählt. Dabei weisen Verdampferrohre 10, die beim Betrieb des Durchlaufdampferzeugers 2 einer stärkeren Beheizung ausgesetzt sind, einen größeren Rohrinnendurchmesser D auf als Verdampferrohre 10, die beim Betrieb des Durchlaufdampferzeugers 2 geringer beheizt werden. Damit wird gegenüber dem Fall mit gleichen Rohrinnendurchmessern erreicht, daß sich der Durchsatz des Strömungsmediums S in den Verdampferrohren 10 mit größerem Rohrinnendurchmesser D erhöht und dadurch Temperaturdifferenzen am Austritt der Verdampferrohre 10 infolge unterschiedlicher Beheizung reduziert werden. Eine weitere Maßnahme, die Durchströmung der Verdampferrohre 10 mit Strömungsmedium S an die Beheizung anzupassen, ist der Einbau von Drosseleinrichtungen in einen Teil der Verdampferrohre 10 und/oder in das zur Zuführung von Strömungsmedium S vorgesehene Leitungssystem 19. Um dagegen die Beheizung an den Durchsatz des Strömungsmediums S durch die Verdampferrohre 10 anzupassen, kann die Flossenbreite in Abhängigkeit von der Position der Verdampferrohre 10 in der Brennkammer 4 gewählt werden. Alle genannten Maßnahmen bewirken trotz stark unterschiedlicher Beheizung der einzelnen 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. Another measure, the flow the evaporator tubes 10 with flow medium S to the heating to adapt, the installation of throttle devices in one Part of the evaporator tubes 10 and / or for the supply of Flow medium S provided line system 19. In contrast the heating to the throughput of the flow medium S. to adjust the evaporator tubes 10, the fin width in Depending on the position of the evaporator tubes 10 in the Combustion chamber 4 can be selected. Effect all of the above measures despite strongly different heating of the individual

Verdampferrohre 10 eine annähernd gleiche spezifische Wärmeaufnahme des in den Verdampferrohen 10 geführten Strömungsmediums S beim Betrieb des Durchlaufdampferzeugers 2 und somit nur geringe Temperaturdifferenzen an deren Austritt. Die Inneberippung der Verdampferrohre 10 ist dabei derart ausgelegt, daß eine besonders zuverlässige Kühlung der Verdampferrohre 10 trotz unterschiedlicher Beheizung und Durchströmung mit Strömungsmedium S bei allen Lastzuständen des Durchlaufdampferzeugers 2 gewährleistet ist.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.

Der Horizontalgaszug 6 weist eine Anzahl von als Schottheizflächen ausgebildeten Überhitzerheizflächen 22 auf, die in hängender Bauweise annähernd senkrecht zur Hauptströmungsrichtung 24 des Heizgases G angeordnet und deren Rohre für eine Durchströmung des Strömungsmediums S jeweils parallel geschaltet sind. Die Überhitzerheizflächen 22 werden überwiegend konvektiv beheizt und sind strömungsmediumsseitig den Verdampferrohren 10 der Brennkammer 4 nachgeschaltet.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.

Der Vertikalgaszug 8 weist eine Anzahl von überwiegend konvektiv beheizbaren Konvektionsheizflächen 26 auf, die aus annähernd senkrecht zur Hauptströmungsrichtung 26 des Heizgases G angeordneten Rohren gebildet sind. Diese Rohre sind für eine Durchströmung des Strömungsmediums S jeweils parallel geschaltet. Außerdem ist in dem Vertikalgaszug 8 ein Economizer 28 angeordnet. Ausgangsseitig mündet der Vertikalgaszug 8 in einen weiteren Wärmetauscher, beispielsweise in einen Luftvorwärmer und von dort über einen Staubfilter in einen Kamin. Die dem Vertikalgaszug 8 nachgeschalteten Bauteile sind in Figur 1 nicht näher dargestellt.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.

Der Durchlaufdampferzeuger 2 ist mit einer horizontalen Brennkammer 4 mit besonders niedriger Bauhöhe ausgeführt und somit mit besonders geringem Herstellungs- und Montageaufwand errichtbar. Hierzu weist die Brennkammer 4 des Durchlaufdampferzeugers 2 eine Anzahl von Brennern 30 für fossilen Brennstoff B auf, die an der Stirnwand 11 der Brennkammer 4 in der Höhe des Horizontalgaszuges 6 angeordnet sind.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. For this purpose, 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.

Damit der fossile Brennstoff B zur Erzielung eines besonders hohen Wirkungsgrads besonders vollständig ausbrennt und Materialschäden der heizgasseitig gesehen ersten Überhitzerheizfläche 22 des Horizontalgaszuges 6 und eine Verschmutzung derselben, beispielsweise durch Eintrag von schmelzflüssiger Asche mit hoher Temperatur, besonders zuverlässig verhindert sind, ist die Länge L der Brennkammer 4 derart gewählt, daß sie die Ausbrandlänge des Brennstoffs B beim Vollastbetrieb des Durchlaufdampferzeugers 2 übersteigt. Die Länge L ist dabei der Abstand von der Stirnwand 11 der Brennkammer 4 zum Eintrittsbereich 32 des Horizontalgaszugs 6. Die Ausbrandlänge des Brennstoffs B ist dabei definiert als die Heizgasgeschwindigkeit in horizontaler Richtung bei einer bestimmten mittleren Heizgastemperatur multipliziert mit der Ausbrandzeit tA der Flamme F des Brennstoffs B. Die für den jeweiligen Durchlaufdampferzeuger 2 maximale Ausbrandlänge ergibt sich beim Vollastbetrieb des jeweiligen Durchlaufdampferzeugers 2. Die Ausbrandzeit tA der Flamme F des Brennstoffs B wiederum ist die Zeit, die beispielsweise ein Kohlenstaubkorn mittlerer Größe zum vollständigen Ausbrennen bei einer bestimmten mittleren Heizgastemperatur benötigt.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 ,

Um eine besonders günstige Ausnutzung der Verbrennungswärme des fossilen Brennstoffs B zu gewährleisten, ist die Länge L (angegeben in m) der Brennkammer 4 in Abhängigkeit von der Austrittstemperatur TBRK (angegeben in °C) des Heizgases G aus der Brennkammer 4, der Ausbrandzeit tA (angegeben in s) der Flamme F des Brennstoffs B und dem Dampfstrom M (angegeben in kg/s) des Durchlaufdampferzeugers 2 bei Vollast geeignet gewählt. Diese horizontale Länge L der Brennkammer 4 beträgt dabei mindestens 80 % der Höhe H der Brennkammer 4. Die Höhe H wird dabei von der Trichteroberkante der Brennkammer 4, in Figur 1 durch die Linie mit den Endpunkten X und Y markiert, bis zur Brennkammerdecke gemessen. Die Länge L der Brennkammer 4 bestimmt sich näherungsweise über die Funktionen (1) und (2): L (M, tA) = (C1 + C2 · M) · tA und L (M, TBRK) = (C3 · TBRK + C4)M + C5(TBRK)2 + C6 · TBRK + C7 mit
C1 = 8 m/s   und
C1 = 8 m/s   und
C2 = 0,0057 m/kg   und
C3 = -1,905 · 10-4 (m · s)/(kg°C)   und
C4 = 0,286 (s · m)/kg   und
C5 = 3 · 10-4 m/(°C)2   und
C6 = -0,842 m/°C   und
C7 = 603,41 m.In order to ensure a particularly favorable utilization of the heat of combustion of the fossil fuel B, 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 length L of the combustion chamber 4 is approximately determined by the functions (1) and (2): L (M, t A ) = (C 1 + C 2 · M) · t A and L (M, T BRK ) = (C 3 · T BRK + C 4 ) M + C 5 (T BRK ) 2 + C 6 · T BRK + C7 With
C 1 = 8 m / s and
C 1 = 8 m / s and
C 2 = 0.0057 m / kg and
C 3 = -1.905 x 10 -4 (ms) / (kg ° C) and
C 4 = 0.286 (s · m) / kg and
C 5 = 3 · 10 -4 m / (° C) 2 and
C 6 = -0.842 m / ° C and
C 7 = 603.41 m.

Näherungsweise ist hierbei als eine zulässige Abweichung um +20%/-10% vom durch die jeweilige Funktion definierten Wert zu verstehen. Dabei gilt bei der Auslegung des Durchlaufdampferzeugers 2 für ein vorgegebenen Dampfstrom M des Durchlaufdampferzeugers 2 bei Vollast der größere Wert aus den Funktionen (1) und (2) für die Länge L der Brennkammer 4.Approximately this is a permissible deviation +20% / - 10% of the value defined by the respective function to understand. The following applies to the design of the once-through steam generator 2 for a given steam flow M des Continuous steam generator 2 at full load the larger value the functions (1) and (2) for the length L of the combustion chamber 4.

Als Beispiel für eine mögliche Auslegung des Durchlaufdampferzeugers 2 sind für einige Längen L der Brennkammer 4 in Abhängigkeit von dem Dampfstrom M des Durchlaufdampferzeugers 2 bei Vollast in das Koordinatensystem gemäß Figur 3 sechs Kurven K1 bis K6 eingezeichnet. Dabei sind den Kurven jeweils folgende Parameter zugeordnet:

  • K1: tA = 3s   gemäß (1),
  • K2: tA = 2,5s   gemäß (1),
  • K3: tA = 2s   gemäß (1),
  • K4: TBRK = 1200°C   gemäß (2),
  • K5: TBRK = 1300°C   gemäß (2),
  • K6: TBRK = 1400°C   gemäß (2).
    • As an example of a possible design of the continuous steam generator 2, six curves K 1 to K 6 are drawn for some lengths L of the combustion chamber 4 as a function of the steam flow M of the continuous steam generator 2 at full load in the coordinate system according to FIG. The following parameters are assigned to the curves:
  • K 1 : t A = 3s according to (1),
  • K 2 : t A = 2.5 s according to (1),
  • K 3 : t A = 2s according to (1),
  • K 4 : T BRK = 1200 ° C according to (2),
  • K 5 : T BRK = 1300 ° C according to (2),
  • K 6 : T BRK = 1400 ° C according to (2).

    • Zur Bestimmung der Länge L der Brennkammer 4 sind somit beispielsweise für eine Ausbrandzeit tA = 3s und eine Austrittstemperatur TBRK = 1200°C des Heizgases G aus der Brennkammer 4 die Kurven K1 und K4 heranzuziehen. Daraus ergibt sich bei einem vorgebenen Dampfstrom M des Durchlaufdampferzeugers 2 bei Vollast

  • von M = 80 kg/s eine Länge von L = 29 m gemäß K4,
  • von M = 160 kg/s eine Länge von L = 34 m gemäß K4,
  • von M = 560 kg/s eine Länge von L = 57 m gemäß K4.
    • To determine the length L of the combustion chamber 4, the curves K 1 and K 4 are thus to be used, for example, for a burnout time t A = 3 s and an exit temperature T BRK = 1200 ° C. of the heating gas G from the combustion chamber 4. This results in a given steam flow M of the continuous steam generator 2 at full load
  • from M = 80 kg / s a length of L = 29 m according to K 4 ,
  • from M = 160 kg / s a length of L = 34 m according to K 4 ,
  • from M = 560 kg / s a length of L = 57 m according to K 4 .

    • Es gilt also stets die als durchgezogene Linie gezeichnete Kurve K4.The curve K 4 drawn as a solid line always applies.

    Für die Ausbrandzeit tA = 2,5s der Flamme F des Brennstoffs B und die Austrittstemperatur des Heizgases G aus der Brennkammer TBRK = 1300°C sind beispielsweise die Kurven K2 und K5 heranzuziehen. Daraus ergibt sich bei einem vorgegebenen Dampfstrom M des Durchlaufdampferzeugers 2 bei Vollast

  • von M = 80 kg/s eine Länge von L = 21 m gemäß K2,
  • von M = 180 kg/s eine Länge von L = 23 m gemäß K2 und K5,
  • von M = 560 kg/s eine Länge von L = 37 m gemäß K5.
    • For the burnout time t A = 2.5 s of the flame F of the fuel B and the exit temperature of the heating gas G from the combustion chamber T BRK = 1300 ° C., the curves K 2 and K 5 are to be used, for example. For a given steam flow M of the continuous steam generator 2, this results at full load
  • from M = 80 kg / s a length of L = 21 m according to K 2 ,
  • from M = 180 kg / s a length of L = 23 m according to K 2 and K 5 ,
  • from M = 560 kg / s a length of L = 37 m according to K 5 .

    • Es gilt also bis M = 180 kg/s der Teil der Kurve K2, die als durchgezogene Linie gezeichnet ist und nicht die in diesem Wertebereich von M als gestrichelte Linie gezeichnete Kurve K5. Für Werte von M, die größer als 180 kg/s sind, gilt der Teil der Kurve K5, der als durchgezogene Linie gezeichnet ist und nicht die in diesem Wertebereich von M als gestrichelte Linie gezeichnete Kurve K2.Up to M = 180 kg / s, the part of the curve K 2 that is drawn as a solid line and not the curve K 5 drawn as a dashed line in this value range of M applies. For values of M that are greater than 180 kg / s, the part of the curve K 5 that is drawn as a solid line applies and not the curve K 2 drawn as a dashed line in this value range of M.

    Der Ausbrandzeit tA = 2s der Flamme F des Brennstoffs B und der Austrittstemperatur des Heizgases G aus der Brennkammer TBRK = 1400°C sind beispielsweise die Kurven K3 und K6 zugeordnet. Daraus ergibt sich bei einem vorgegebenen Dampfstrom M des Durchlaufdampferzeugers 2 bei Vollast

  • von M = 80 kg/s eine Länge von L = 18 m gemäß K3,
  • von M = 465 kg/s eine Länge von L = 21 m gemäß K3 und K6,
  • von M = 560 kg/s eine Länge von L = 23 m gemäß K6.
    • The burnout time t A = 2s of the flame F of the fuel B and the exit temperature of the heating gas G from the combustion chamber T BRK = 1400 ° C. are assigned to the curves K 3 and K 6 , for example. For a given steam flow M of the continuous steam generator 2, this results at full load
  • from M = 80 kg / s a length of L = 18 m according to K 3 ,
  • from M = 465 kg / s a length of L = 21 m according to K 3 and K 6 ,
  • from M = 560 kg / s a length of L = 23 m according to K 6 .

    • Es gilt also für Werte von M bis 465 kg/s die als durchgezogene Linie in diesem Bereich gezeichnete Kurve K3 und nicht die als gestrichelte Linie in diesem Bereich gezeichnete Kurve K6. Für Werte von M die größer als 465 kg/s sind gilt der Teil der als durchgezogene Linie gezeichneten Kurve K6 und nicht der Teil der als gestrichelte Linie gezeichneten Kurve K3.For values from M to 465 kg / s, the curve K 3 drawn as a solid line in this area and not the curve K 6 drawn as a dashed line in this area applies. For values of M which are greater than 465 kg / s, the part of the curve K 6 drawn as a solid line and not the part of the curve K 3 drawn as a broken line applies.

    Damit sich beim Betrieb des Durchlaufdampferzeugers 2 in einem mehrbeheizten Verdampferrohr 10 selbsttätig ein höherer Durchsatz des Strömungsmediums S einstellt als in einem minderbeheizten Verdampferrohr 10, ist für eine Anzahl N von parallel geschalteten Verdampferrohren 10 der Quotient aus dem Dampfstrom M (angegeben in kg/s) des Durchlaufdampferzeugers 2 bei Vollast und der Summe A (angegeben in m2) der Innenquerschnittsfläche der Anzahl N dieser parallel mit Strömungsmedium S beaufschlagbaren Verdampferrohre 10 mit jeweils einem Rohrinnendurchmesser DN so gewählt, daß die Bedingung

    Figure 00200001
    erfüllt ist. Dabei ist die Zahl 1350 in kg/sm2 angegeben und DN der Rohrinnendurchmesser des N-ten Verdampferrohrs 10 mit i = 1 bis N.In order for a higher throughput of the flow medium S to set itself automatically in a multi-heated evaporator tube 10 when the continuous steam generator 2 is operating than in a less heated evaporator tube 10, 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
    Figure 00200001
    is satisfied. The number 1350 is given in kg / sm 2 and D N is the inside diameter of the Nth evaporator tube 10 with i = 1 to N.

    Beim Betrieb des Durchlaufdampferzeugers 2 wird den Brennern 30 fossiler Brennstoff B zugeführt. Die Flammen F der Brenner 30 sind dabei horizontal ausgerichtet. Durch die Bauweise der Brennkammer 4 wird eine Strömung des bei der Verbrennung entstehenden Heizgases G in annähernd horizontaler Hauptströmungsrichtung 24 erzeugt. Dieses gelangt über den Horizontalgaszug 6 in den annähernd zum Boden hin ausgerichteten Vertikalgaszug 8 und verläßt diesen in Richtung des nicht näher dargestellten Kamins.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.

    In den Economizer 28 eintretendes Strömungsmedium S gelangt über die in dem Vertikalgaszug 8 angeordneten Konvektionsheizflächen 26 in das Eintrittssammler-System 18 der Verdampferrohre 10 der Brennkammer 4 des Durchlaufdampferzeugers 2. In den vertikal angeordneten, gasdicht miteinander verschweißten Verdampferrohren 10 der Brennkammer 4 des Durchlaufdampferzeugers 2 findet die Verdampfung und gegebenenfalls eine teilweise Überhitzung des Strömungsmediums S statt. Der dabei entstehende Dampf bzw. ein Wasser-Dampf-Gemisch wird in dem Austrittssammler-System 20 für Strömungsmedium S gesammelt. Von dort gelangt der Dampf bzw. das Wasser-Dampf-Gemisch. über die Wände des Horizontalgaszugs 6 und des Vertikalgaszugs 8 in die Überhitzerheizflächen 22 des Horizontalgaszuges 6. In den Überhitzerheizflächen 22 erfolgt eine weitere Überhitzung des Dampfs, der anschließend einer Nutzung, beispielsweise dem Antrieb einer Dampfturbine, zugeführt wird.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. In the vertically arranged, gas-tight welded together 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. In 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.

    Mit der Begrenzung des Quotienten aus dem Dampfstrom M des Durchlaufdampferzeugers 2 bei Vollast und der Summe der Innenquerschnittsflächen F auf den Wert 1350 kg/sm2 für eine Anzahl N von parallel geschalteten Verdampferrohren 10 sind in sonders einfacher Weise besonders geringe Temperaturdifferenzen zwischen benachbarten Verdampferrohren 10 bei gleichzeitig besonders zuverlässiger Kühlung der Verdampferrohre 10 bei allen Lastzuständen des Durchlaufdampferzeugers 2 gewährleistet. Zudem ist die Reihenschaltung der Verdampferrohre 10 insbesondere für eine Ausnutzung der annähernd horizontalen Hauptströmungsrichtung 24 des Heizgases G ausgelegt. Dabei ist durch eine Wahl der Länge L der Brennkammer 4 in Abhängigkeit von dem Dampfstrom M des Durchlaufdampferzeugers 2 bei Vollast sichergestellt, daß die Verbrennungswärme des fossilen Brennstoffs B besonders zuverlässig ausgenutzt wird. Außerdem läßt sich der Durchlaufdampferzeuger 2 durch seine besonders geringe Bauhöhe und kompakte Bauweise mit besonders geringem Herstellungs- und Montageaufwand errichten. Dabei kann ein mit vergleichsweise geringem technischen Aufwand ersteilbares Gerüst vorgesehen sein. Bei einer Kraftwerksanlage mit einer Dampfturbine und einem eine derart geringe Bauhöhe aufweisenden Durchlaufdampferzeuger 2 können außerdem die Verbindungsrohre von dem Durchlaufdampferzeuger zu der Dampfturbine in besonders kurzer Weise ausgelegt sein.By limiting the quotient from the steam flow M of the continuous-flow steam generator 2 at full load and the sum of the internal cross-sectional areas F to the value 1350 kg / sm 2 for a number N of evaporator tubes 10 connected in parallel, particularly small temperature differences between adjacent evaporator tubes 10 are particularly simple at the same time ensures particularly reliable cooling of the evaporator tubes 10 in all load states of the continuous steam generator 2. In addition, the series connection of the evaporator tubes 10 is designed in particular for utilizing the approximately horizontal main flow direction 24 of the heating gas G. A choice of the length L of the combustion chamber 4 as a function of the steam flow M of the continuous steam generator 2 at full load ensures that the heat of combustion of the fossil fuel B is used particularly reliably. In addition, 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. In a power plant with a steam turbine and a continuous steam generator 2 having such a low overall height, the connecting pipes from the continuous steam generator to the steam turbine can also be designed in a particularly short manner.

    Claims (14)

    1. Once-through steam generator (2) having a combustion chamber (4) for the fossil fuel (B), which is followed on the fuel-gas side, via a horizontal gas flue (6), by a vertical gas flue (8), the containment walls (9) of the combustion chamber (4) being formed from vertically arranged evaporator tubes (10) welded to one another in a gas-tight manner, and the combustion chamber (4), comprising a number of burners (30) arranged level with the horizontal gas flue (6) and being designed in such a way that, in each case for a number (N) of evaporator tubes (10) of the combustion chamber (4) which are capable of being acted upon in parallel by flow medium (S) and which, on the flow-medium side, are in each case preceded by a common inlet-header system (18) for flow medium (S) and followed by a common outlet-header system (20), the quotient formed from the steam stream (M) (given in kg/s) under full load and from the sum (A) (given in m2) of the inner cross-sectional areas of these evaporator tubes (10) capable of being acted upon in parallel by the flow medium (S) is lower than 1350 (given in kg/sm2), and in which a number of the evaporator tubes (10) carry on their inside in each case ribs (40) forming a multi-flight thread.
    2. Once-through steam generator (2) according to Claim 1, in which the evaporator tubes (10) of the end wall (11) of the combustion chamber (4) precede, on the flow-medium side, the evaporator tubes (10) of the other containment walls (9) of the combustion chamber (4).
    3. Once-through steam generator (2) according to one of Claims 1 and 2, in which the tube inside diameter (D) of a number of the evaporator tubes (10) of the combustion chamber (4) is selected as a function of the respective position of the evaporator tubes (10) in the combustion chamber (4).
    4. Once-through steam generator (2) according to Claim 3, in which a pitch angle (α) between a plane (42) perpendicular to the tube axis and the flanks (44) of the ribs (40) arranged on the tube inside is smaller than 60°, preferably smaller than 55°.
    5. Once-through steam generator (2) according to one of Claims 1 to 4, in which a number of the evaporator tubes (10) in each case have a throttle device.
    6. Once-through steam generator (2) according to one of Claims 1 to 5, in which a line system (19) for feeding flow medium (S) into the evaporator tubes (10) of the combustion chamber (4) is provided, the line system (19) having a number of throttle devices, in particular throttle fittings, for reducing the throughflow of the flow medium (S).
    7. Once-through steam generator (2) according to one of Claims 1 to 6, in which the side walls (12) of the horizontal gas flue (6) are formed from vertically arranged steam generator tubes (16) welded to one another in a gas-tight manner and capable of being acted upon in parallel by flow medium (S).
    8. Once-through steam generator (2) according to one of Claims 1 to 7, in which the side walls (14) of the vertical gas flue (8) are formed from vertically arranged steam generator tubes (17) welded to one another in a gas-tight manner and capable of being acted upon in parallel by flow medium (S).
    9. Once-through steam generator (2) according to one of Claims 1 to 8, in which adjacent evaporator or steam generator tubes (10, 16, 17) are welded to one another in a gas-tight manner via fins, the fin width being selected as a function of the respective position of the evaporator or steam generator tubes (10, 16, 17) in the combustion chamber (4) of the horizontal gas flue (6) and/or of the vertical gas flue (8).
    10. Once-through steam generator (2) according to one of Claims 1 to 9, in which a number of superheater heating surfaces (22) are arranged in a suspended form of construction in the horizontal gas flue (6).
    11. Once-through steam generator (2) according to one of Claims 1 to 10, in which a number of convection heating surfaces (26) are arranged in the vertical gas flue (8).
    12. Once-through steam generator (2) according to one of Claims 1 to 11, in which the burners (30) are arranged on the end wall (11) of the combustion chamber (4).
    13. Once-through steam generator (2) according to one of Claims 1 to 12, in which the length (L) of the combustion chamber (4), defined by the distance from the end wall (11) of the combustion chamber (4) to the inlet region (32) of the horizontal gas flue (6), is at least equal to the burn-up length of the fuel (B) when the steam generator (2) is operating under full load.
    14. Once-through steam generator (2) according to one of Claims 1 to 13, in which the length L (given in m) of the combustion chamber (4) is selected as a function of the steam stream M (given in kg/s) under full load, of the burn-up time tA (given in s) of the flame (F) of the fuel (B) and/or of the outlet temperature TBRK (given in °C) of the fuel gas (G) of the combustion chamber (4) approximately according to the functions L (M, tA) = (C1 + C2 · M) · tA and L (M, TBRK) = (C3 · TBRK + C4)M + C5(TBRK)2 + C6 · TBRK + C7 with C1 = 8 m/s and C2 = 0.0057 m/kg and C3 = -1.905 · 10-4 (m · s)/(kg°C) and C4 = 0.286 (s · m)/kg and C5 = 3 · 10-4 m/ (°C)2 and C6 = -0.842 m/°C and C7 = 603.41 m, the higher value of the length (L) of the combustion chamber (4) applying in each case to a predetermined steam stream (M) under full load.
    EP99964411A 1998-12-18 1999-12-06 Fossil fuel fired continuous-flow steam generator Expired - Lifetime EP1141625B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE19858780A DE19858780C2 (en) 1998-12-18 1998-12-18 Fossil-heated continuous steam generator
    DE19858780 1998-12-18
    PCT/DE1999/003896 WO2000037851A1 (en) 1998-12-18 1999-12-06 Fossil fuel fired continuos-flow steam generator

    Publications (2)

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

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    ID=7891779

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP99964411A Expired - Lifetime EP1141625B1 (en) 1998-12-18 1999-12-06 Fossil fuel fired continuous-flow steam generator

    Country Status (12)

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

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    US20050072379A1 (en) * 2003-08-15 2005-04-07 Jupiter Oxygen Corporation Device and method for boiler superheat temperature control
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    EP2065641A3 (en) * 2007-11-28 2010-06-09 Siemens Aktiengesellschaft Method for operating a continuous flow steam generator and once-through steam generator
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    Also Published As

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

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