EP2601441A2 - Forced-flow steam generator - Google Patents

Forced-flow steam generator

Info

Publication number
EP2601441A2
EP2601441A2 EP11725739.4A EP11725739A EP2601441A2 EP 2601441 A2 EP2601441 A2 EP 2601441A2 EP 11725739 A EP11725739 A EP 11725739A EP 2601441 A2 EP2601441 A2 EP 2601441A2
Authority
EP
European Patent Office
Prior art keywords
steam generator
tubes
forced
steam
generator tubes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11725739.4A
Other languages
German (de)
French (fr)
Other versions
EP2601441B1 (en
Inventor
Joachim Brodesser
Jan BRÜCKNER
Martin Effert
Joachim Franke
Tobias Schulze
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP2601441A2 publication Critical patent/EP2601441A2/en
Application granted granted Critical
Publication of EP2601441B1 publication Critical patent/EP2601441B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F22B29/061—Construction of tube walls
    • F22B29/062—Construction of tube walls involving vertically-disposed water tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • 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
    • F22B21/36—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 involving an upper drum or headers mounted at the top of the combustion chamber
    • 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
    • F22B21/36—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 involving an upper drum or headers mounted at the top of the combustion chamber
    • F22B21/366—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 involving an upper drum or headers mounted at the top of the combustion chamber involving a horizontal drum mounted in the middle of the boiler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/02—Steam boilers of forced-flow type of forced-circulation type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/62—Component parts or details of steam boilers specially adapted for steam boilers of forced-flow type
    • F22B37/70—Arrangements for distributing water into water tubes
    • F22B37/74—Throttling arrangements for tubes or sets of tubes

Definitions

  • the invention relates to a forced once-through steam generator with a surrounding gas-tight welded, formed in the vertical direction steam generator tubes wall, in which a fürgangs ⁇ collector is arranged within the enclosure, the first plurality of parallel switched steam generator tubes outlet side with a two ⁇ th, the first A plurality of series connected downstream plurality of steam generator tubes connected on the inlet side flow medium side. It further relates to a power plant with such a steam generator.
  • a steam generator is a plant for producing steam from a flow medium.
  • a fluid medium typically water is heated, and vice ⁇ converts into steam.
  • the steam is then used to drive machinery or generate electrical energy.
  • a steam generator comprises an evaporator for generating the steam and a superheater, in which the steam is heated to the temperature required for the consumer.
  • the evaporator is preceded by a preheater for the use of waste heat, which further increases the efficiency of the overall system.
  • Steam generators are industrially today usually designed as ⁇ serrohrkessel, ie, the flow medium is guided in steam generator tubes.
  • the steam generator tubes can be welded gas-tight with each other and thus form a order ⁇ supervisedswand, within which the heat-supplying hot gas is guided.
  • Steam generators can be designed either in a vertical or horizontal design, ie, the hot gas is guided in the vertical or horizontal direction.
  • Steam generators can furthermore be designed as forced-circulation steam generators, the passage of the flow medium being forced by a feed pump. The flow medium is conveyed by the feed pump into the boiler and successively the preheater, the evaporator and the superheater are flowed through.
  • the tubing of the containment is subdivided into a unte ⁇ ren and an upper section, said lower section includes a first plurality of parallel-connected steam ⁇ generator tubes and the upper portion of a second, the first plurality serially downstream Plural parallel connected steam generator tubes.
  • the lower and upper From ⁇ section are connected by a passage collectors.
  • the invention proceeds from the consideration that the overheating of individual steam generator tubes is due to a unzurei ⁇ sponding derivative of the incoming heat by flow medium. Inadequate heat removal occurs when the steam generator tube in question has too low a mass flow. With a pronounced natural circulation characteristic, with very low inlet steam content and very low heat input, the hydrostatic pressure drop in these tubes is already approximately as large or equal to the total pressure difference between the inlet and outlet of the steam generator tube. The remaining pressure difference as a driving force of the flow is therefore very low or disappears completely, so that in the worst case the flow stagnates.
  • the through-flow collector effects a complete equalization of the pressure, it does not effect complete mixing of the incoming flow medium, which would lead to a compensation of water and vapor content in the steam generator tubes connected downstream of it. Due to the low vapor content of the lower-heated steam generator tubes of the lower section and additional local segregation phenomena in the collector, the steam content can thus still approach zero at certain individual operating conditions when entering individual tubes of the upper vertical bore. Thus, this phenomenon should be be avoided by a sufficient attenuation of NaturumlaufCharakte ⁇ rrick. This can be achieved by increasing the friction pressure loss in the respective steam generator tube. For this purpose, in each case a throttle device should be provided in the steam generator tubes downstream of the throughput collector.
  • the respective throttle device is arranged at the upper outlet of the surrounding wall.
  • the throttle device is simple
  • the surrounding wall of a steam generator in a vertical construction can have different horizontal cross sections. A particularly simple construction is possible if the
  • Cross section is substantially rectangular.
  • the steam generator tubes arranged in the corner regions are heated particularly weakly, since they are furthest away from the center of the hot gas duct and at the same time have a particularly small heat input surface.
  • the vapor content of individual corner tubes of the lower section of the vertical bore can approach zero, so that an unevenly distributed water-vapor mixture enters the intermediate header here. Since the interim 1er also does not cause sufficient mixing here, the mass flow in the downstream corner pipes can come to a standstill and the heat dissipation thus be insufficient.
  • teilhaft note the downstream of the flow collector steam generator tubes on a throttle device.
  • the passage collector may be continuous circumferentially arranged horizontally, that is, it connects all be below ⁇ relationship as above arranged steam generator tubes of the surrounding wall with each other. Despite the complete pressure equalization over all pipes, segregation of water and steam can still occur. Accordingly, such a forced-circulation steam generator also advantageously has a throttle device in each of the steam generator tubes connected downstream of the through-flow collector.
  • the tubing below the passage collector can be configured in a spiral shape.
  • the tubes run circumferentially around the entire enclosure wall. Although this causes a more complex construction and also a smaller number of steam generator tubes in the lower area, but this heating differences in various areas of the enclosure wall are largely compensated. Nevertheless, he was ⁇ known that even with such a construction in the through-collector to random local segregation can occur, which cause the above-described problems of too low a mass flow in the pipes downstream of the through-collector. Therefore, even with such a construction, advantageously the steam generator tubes connected downstream of the throughflow collector each have a throttle device.
  • the forced-circulation steam generator is followed by a steam turbine, for example for generating electricity, downstream of the flow medium.
  • a power plant advantageously has such a steam ⁇ generator.
  • insbesonde re the arrangement of a throttle device in the passage collector downstream steam generator tubes a forced flow steam generator sufficient heat dissipation in each tube is guaranteed and thus inadmissible high temperatures that can damage the pipe wall, be avoided.
  • This measure is based on the realization that even in a forced continuous steam generator a non-negligible natural circulation characteristic is present, which is weakened by the arrangement of throttles. Ultimately, this restriction in the operation of a power plant avoided.
  • FIG. 2 shows a graphical representation of the mass flow density and the fluid temperature at the outlet of a comparatively weakly heated corner tube of the once-through steam generator with and without throttle device.
  • FIG. 1 schematically shows a fossil-fired, vertically bored forced once-through steam generator 1 according to the invention.
  • the once-through steam generator 1 comprises an enclosing wall 4 formed from gas-tightly welded steam generator tubes 2.
  • the enclosing wall 4 has a substantially rectangular horizontal cross-section 6.
  • a combustion chamber 8 is arranged with a number of burners not shown in detail for the combustion of a fossil fuel, which provide the heat supply to the steam generator tubes 4.
  • the enclosure wall 4 is divided into an upper portion 10 and ei ⁇ NEN lower portion 12, wherein the portions 10 and 12 are connected to each other via a through-collector 14.
  • the tubing in the lower portion 12 is arranged vertically here, but may also be arranged spirally around the Um chargedswand circumferentially.
  • the passage collector 14 collects all of the flow medium exiting from the steam generator tubes 2 of the lower section 12 and thus enables a pressure equalization between the parallel connected
  • the heat generated by the burner is largely absorbed by heat radiation through the steam generator tubes 2.
  • the passage collector 14 now effects a complete pressure equalization, however, no complete mixing of the incoming flow medium. Due to the described low vapor content at the exit from the corner tubes 16 of the lower section 12 as well as additional local segregation phenomena in the passage header 14, the vapor content at the entrance to individual steam generator tubes 2 of the upper section 10 can become very small.
  • throttling devices 18 are arranged in the exemplary embodiment at the outlet of all the steam generator tubes of the upper region 10, with only individual throttle devices 18 being shown by way of example in order to simplify the illustration.
  • the throttle devices 18 are each designed as a diaphragm, whereby the total pressure loss is increased for all parallel tubes. This results in that the hydrostatic pressure drop in the jewei ⁇ then steam generator tubes 2, in particular in the corner tubes 16 is reduced in relative terms. Thus, a reaching out ⁇ pressure difference always remains available as a driving force of the flow. This effect is illustrated by FIG. 2:
  • FIG. 2 shows a graphical representation of the parameters of the flow medium in a corner pipe 16 of the upper portion 10 with and without throttle device 18 at comparatively low ger supply of heat and for a partial load operation of Dampferzeu ⁇ gers 1.
  • the left-hand scale shows the mass flow density in the corner ⁇ pipe 16 in kilograms per square meter and second (kg / m2s), in the right scale shows the fluid temperature at the outlet of the Corner tube 16 in degrees Celsius (° C), each plotted against the vapor content of the flow medium at the tube inlet.
  • Curve 20 shows the mass flow density in the corner tube 16 without a separate throttle device 18.
  • the drop of the curve 20 to the left of the graph clearly shows how toward lower Dampfanfeilen the mass flow density in the corner tube 16 decreases.
  • the mass flow density drops to a value of 40 kg / m2s, which practically equates to a stagnation of the flow in the pipe.
  • a sufficient heat dissipation in the pipe is no longer guaranteed and accordingly increases the temperature of the flow medium and thus of the corner tube 16 from a Dampfan ⁇ part of about 0.2 significantly, as curve 22 represents.

Abstract

A forced-flow steam generator (1) having a surrounding wall (4) formed from steam generator pipes (2) which are welded in a gas-tight fashion and traversable by flow in the vertical direction, in which within the surrounding wall (4) there is arranged a passage collector (14) by means of which the outlet side of a first multiplicity of steam generator pipes (2) in parallel configuration is connected at the flow medium side to the inlet side of a second multiplicity, in series configuration with and downstream of the first multiplicity, of steam generator pipes (2) in parallel configuration, should have a particularly long service life and particularly low susceptibility to faults, independently of the operating state. For this purpose, the steam generator pipes (16) arranged downstream of the passage collector (14) have in each case one restrictor device (18).

Description

Beschreibung description
Zwangdurchlaufdampferzeuger Die Erfindung betrifft einen Zwangdurchlaufdampferzeuger mit einer aus gasdicht verschweißten, in vertikaler Richtung durchströmbaren Dampferzeugerrohren gebildeten Umfassungswand, bei dem innerhalb der Umfassungswand ein Durchgangs¬ sammler angeordnet ist, der eine erste Mehrzahl parallel ge- schalteter Dampferzeugerrohre austrittsseitig mit einer zwei¬ ten, der ersten Mehrzahl seriell nachgeschalteten Mehrzahl parallel geschalteter Dampferzeugerrohre eintrittsseitig strömungsmediumsseitig verbindet. Sie betrifft weiter eine Kraftwerksanlage mit einem derartigen Dampferzeuger. The invention relates to a forced once-through steam generator with a surrounding gas-tight welded, formed in the vertical direction steam generator tubes wall, in which a Durchgangs ¬ collector is arranged within the enclosure, the first plurality of parallel switched steam generator tubes outlet side with a two ¬ th, the first A plurality of series connected downstream plurality of steam generator tubes connected on the inlet side flow medium side. It further relates to a power plant with such a steam generator.
Ein Dampferzeuger ist eine Anlage zur Erzeugung von Dampf aus einem Strömungsmedium. In einer solchen Anlage wird ein Strömungsmedium, typischerweise Wasser erhitzt und in Dampf umge¬ wandelt. Der Dampf wird dann für den Antrieb von Maschinen oder zur Erzeugung elektrischer Energie verwendet. Üblicherweise umfasst ein Dampferzeuger einen Verdampfer zur Erzeugung des Dampfes sowie einen Überhitzer, in dem der Dampf auf die für den Verbraucher benötigte Temperatur erhitzt wird. Häufig ist dem Verdampfer ein Vorwärmer zur Nutzung von Ab- wärme vorgeschaltet, der den Wirkungsgrad der Gesamtanlage weiter erhöht. A steam generator is a plant for producing steam from a flow medium. In such a system is a fluid medium, typically water is heated, and vice ¬ converts into steam. The steam is then used to drive machinery or generate electrical energy. Typically, a steam generator comprises an evaporator for generating the steam and a superheater, in which the steam is heated to the temperature required for the consumer. Frequently, the evaporator is preceded by a preheater for the use of waste heat, which further increases the efficiency of the overall system.
Dampferzeuger sind industriell heute üblicherweise als Was¬ serrohrkessel ausgeführt, d. h., das Strömungsmedium ist in Dampferzeugerrohren geführt. Die Dampferzeugerrohre können dabei miteinander gasdicht verschweißt werden und so eine Um¬ fassungswand bilden, innerhalb derer das die Wärme zuführende Heißgas geführt wird. Dampferzeuger können entweder in stehender oder liegender Bauweise ausgeführt sein, d. h., das Heißgas wird in vertikaler bzw. horizontaler Richtung geführt . Dampferzeuger können weiterhin als Zwangdurchlaufdampferzeu- ger ausgelegt sein, wobei der Durchlauf des Strömungsmediums von einer Speisepumpe erzwungen wird. Das Strömungsmedium wird dabei von der Speisepumpe in den Kessel gefördert und nacheinander werden der Vorwärmer, der Verdampfer und der Überhitzer durchströmt. Die Erwärmung des Speisewassers bis zur Sattdampftemperatur, die Verdampfung und Überhitzung erfolgen kontinuierlich in einem Durchlauf, so dass - zumindest im Volllastbetrieb - keine gesonderte Abscheideeinrichtung für Wasser und Dampf erforderlich ist. Durchlaufdampferzeuger können auch bei überkritischen Drücken betrieben werden. Die Definitionen der einzelnen Heizflächen Vorwärmer, Verdampfer und Überhitzer sind streng genommen bei dieser Betriebsweise nicht mehr sinnvoll, da ein kontinuierlicher Phasenübergang stattfindet . Steam generators are industrially today usually designed as ¬ serrohrkessel, ie, the flow medium is guided in steam generator tubes. The steam generator tubes can be welded gas-tight with each other and thus form a order ¬ fassungswand, within which the heat-supplying hot gas is guided. Steam generators can be designed either in a vertical or horizontal design, ie, the hot gas is guided in the vertical or horizontal direction. Steam generators can furthermore be designed as forced-circulation steam generators, the passage of the flow medium being forced by a feed pump. The flow medium is conveyed by the feed pump into the boiler and successively the preheater, the evaporator and the superheater are flowed through. The heating of the feed water to the saturated steam temperature, the evaporation and superheating occur continuously in one pass, so that - at least in full load operation - no separate separation device for water and steam is required. Continuous steam generators can also be operated at supercritical pressures. The definitions of the individual heating surfaces preheater, evaporator and superheater are strictly speaking no longer useful in this mode of operation, as a continuous phase transition takes place.
In einer Variante des senkrecht berohrten Durchlaufdampf- erzeugers ist die Berohrung der Umfassungswand in einen unte¬ ren und einen oberen Abschnitt unterteilt, wobei der untere Abschnitt eine erste Mehrzahl parallel geschalteter Dampf¬ erzeugerrohre umfasst und der obere Abschnitt eine zweite, der ersten Mehrzahl seriell nachgeschaltete Mehrzahl parallel geschalteter Dampferzeugerrohre . Der untere und der obere Ab¬ schnitt sind durch einen Durchgangssammler miteinander verbunden. Dadurch wird einerseits ein Druckausgleich zwischen den parallel geschalteten Dampferzeugerrohren erreicht, andererseits auch eine zumindest partielle Durchmischung des Strömungsmediums aus unterschiedlichen Dampferzeugerrohren . In a variant of vertically tubed Durchlaufdampf- generator, the tubing of the containment is subdivided into a unte ¬ ren and an upper section, said lower section includes a first plurality of parallel-connected steam ¬ generator tubes and the upper portion of a second, the first plurality serially downstream Plural parallel connected steam generator tubes. The lower and upper From ¬ section are connected by a passage collectors. As a result, on the one hand pressure equalization between the parallel connected steam generator tubes is achieved, on the other hand, an at least partial mixing of the flow medium from different steam generator tubes.
Bei derartigen Durchlaufdampferzeugern mit in vertikaler Richtung durchströmbaren Dampferzeugerrohren und Durchgangssammler wurde nunmehr festgestellt, dass einzelne Rohre des oberen Abschnitts der Umfassungswand unzulässig hohe Tempera¬ turen annehmen können, was unter Umständen zu einer Zerstörung der Rohrwand führen kann. Dabei ist das Auftreten dieser überhöhten Temperaturen an bestimmte Betriebsparameter geknüpft . Der Erfindung liegt daher die Aufgabe zu Grunde, einen Zwangdurchlaufdampferzeuger der oben genannten Art anzugeben, der unabhängig vom Betriebszustand eine besonders lange Lebens¬ dauer und eine besonders geringe Reparaturanfälligkeit auf- weist. In such continuous steam generators with through-flow in the vertical direction steam generator tubes and through-collector has now been found that individual tubes of the upper portion of the perimeter wall can assume unacceptably high tempera ¬ tures, which can lead to destruction of the pipe wall under certain circumstances. The occurrence of these excessive temperatures is linked to certain operating parameters. The invention is therefore based on the object to provide a forced once- through steam generator of the type mentioned above, which has a particularly long life ¬ life and a particularly low susceptibility to repair regardless of the operating condition.
Diese Aufgabe wird erfindungsgemäß gelöst, indem die dem Durchgangssammler nachgeschalteten Dampferzeugerrohre jeweils eine Drosseleinrichtung aufweisen. This object is achieved according to the invention in that the steam generator tubes connected downstream of the through-flow collector each have a throttle device.
Die Erfindung geht dabei von der Überlegung aus, dass die Überhitzung einzelner Dampferzeugerrohre auf eine unzurei¬ chende Ableitung der eintretenden Wärme durch Strömungsmedium zurückzuführen ist. Eine unzureichende Wärmeabfuhr tritt dann auf, wenn das betreffende Dampferzeugerrohr einen zu niedrigen Massenstrom aufweist. Bei einer ausgeprägten Naturumlauf- Charakteristik ist bei sehr niedrigem Eintrittsdampfgehalt und sehr geringer Wärmezufuhr der hydrostatische Druckabfall in diesen Rohren bereits annähernd so groß oder gleich groß wie die gesamte Druckdifferenz zwischen Eintritt und Austritt des Dampferzeugerrohrs . Die verbleibende Druckdifferenz als treibende Kraft der Strömung ist demnach sehr gering oder verschwindet ganz, so dass im schlimmsten Fall die Strömung stagniert . The invention proceeds from the consideration that the overheating of individual steam generator tubes is due to a unzurei ¬ sponding derivative of the incoming heat by flow medium. Inadequate heat removal occurs when the steam generator tube in question has too low a mass flow. With a pronounced natural circulation characteristic, with very low inlet steam content and very low heat input, the hydrostatic pressure drop in these tubes is already approximately as large or equal to the total pressure difference between the inlet and outlet of the steam generator tube. The remaining pressure difference as a driving force of the flow is therefore very low or disappears completely, so that in the worst case the flow stagnates.
Zwar sollte der Durchgangssammler einen gewissen Ausgleich zwischen den ihm nachgeschalteten Rohren bewirken, um diesen Effekt abzuschwächen. Es wurde jedoch erkannt, dass der Although the passage collector should bring some balance between the tubes downstream to mitigate this effect. However, it was recognized that the
Durchgangssammler zwar einen vollständigen Druckausgleich be- wirkt, jedoch keine vollständige Durchmischung des eintretenden Strömungsmediums, die zu einem Ausgleich von Wasser- und Dampfanteil in den ihm nachgeschalteten Dampferzeugerrohren führen würde. Aufgrund des niedrigen Dampfgehalts aus den schwächer beheizten Dampferzeugerrohren des unteren Ab- Schnitts sowie zusätzlicher lokaler Entmischungsphänomene im Sammler kann somit trotzdem am Eintritt in einzelne Rohre der oberen Senkrechtbohrung in bestimmten Betriebszuständen der Dampfgehalt gegen Null gehen. Somit sollte dieses Phänomen durch eine ausreichende Abschwächung der NaturumlaufCharakte¬ ristik vermieden werden. Dies ist erreichbar, indem der Reibungsdruckverlust in dem jeweiligen Dampferzeugerrohr erhöht wird. Dazu sollte in den dem Durchgangssammler nachgeschalte- ten Dampferzeugerrohren jeweils eine Drosseleinrichtung vorgesehen sein. Although the through-flow collector effects a complete equalization of the pressure, it does not effect complete mixing of the incoming flow medium, which would lead to a compensation of water and vapor content in the steam generator tubes connected downstream of it. Due to the low vapor content of the lower-heated steam generator tubes of the lower section and additional local segregation phenomena in the collector, the steam content can thus still approach zero at certain individual operating conditions when entering individual tubes of the upper vertical bore. Thus, this phenomenon should be be avoided by a sufficient attenuation of NaturumlaufCharakte ¬ ristik. This can be achieved by increasing the friction pressure loss in the respective steam generator tube. For this purpose, in each case a throttle device should be provided in the steam generator tubes downstream of the throughput collector.
In vorteilhafter Ausgestaltung ist die jeweilige Drosseleinrichtung am oberen Austritt der Umfassungswand angeordnet. Eine derartige Anordnung ermöglicht eine besonders einfacheIn an advantageous embodiment, the respective throttle device is arranged at the upper outlet of the surrounding wall. Such an arrangement allows a particularly simple
Konstruktion des Dampferzeugers und erlaubt gleichzeitig eine Nachrüstung bereits bestehender Anlagen, die das oben beschriebene Problem aufweisen. Vorteilhafterweise ist die Drosseleinrichtung als einfacheConstruction of the steam generator and at the same time allows retrofitting of existing systems that have the problem described above. Advantageously, the throttle device is simple
Blende ausgestaltet. Dies erlaubt eine besonders einfache lo¬ kale Reduzierung der Nennweite des betreffenden Dampferzeu¬ gerrohrs und somit eine einfache Erhöhung des Reibungsdruck¬ verlustes. Auch diese Maßnahme erlaubt eine besonders einfa- che Installation der Drosseleinrichtung zur Reduzierung der NaturumlaufCharakteristik . Aperture designed. This allows a particularly simple lo ¬ kale reducing the nominal size of the relevant Dampferzeu ¬ gerrohrs and thus a simple increase of the friction pressure loss ¬. This measure also allows a particularly simple installation of the throttle device to reduce the natural circulation characteristic.
Die Umfassungswand eines Dampferzeugers in stehender Bauweise kann unterschiedliche horizontale Querschnitte aufweisen. Ei- ne besonders einfache Konstruktion ist möglich, wenn derThe surrounding wall of a steam generator in a vertical construction can have different horizontal cross sections. A particularly simple construction is possible if the
Querschnitt im Wesentlichen rechteckig ist. Bei derartigen Dampferzeugern sind insbesondere die in den Eckbereichen angeordneten Dampferzeugerrohre besonders schwach beheizt, da sie am weitesten vom Zentrum des Heißgaskanals entfernt sind und gleichzeitig eine besonders geringe Wärmeeintragsfläche aufweisen. Dadurch kann der Dampfgehalt einzelner Eckrohre des unteren Abschnitts der Senkrechtberohrung gegen Null gehen, so dass hier ein ungleichmäßig verteiltes Wasser-Dampf- Gemisch in den Zwischensammler eintritt. Da der Zwischensamm- 1er auch hier keine ausreichende Durchmischung bewirkt, kann der Massenstrom in den nachgeschalteten Eckrohren zum Erliegen kommen und der Wärmeabtransport damit unzureichend sein. Gerade bei einem derartigen Dampferzeuger weisen daher vor- teilhafterweise die dem Durchgangssammler nachgeschalteten Dampferzeugerrohre eine Drosseleinrichtung auf. Cross section is substantially rectangular. In such steam generators, in particular, the steam generator tubes arranged in the corner regions are heated particularly weakly, since they are furthest away from the center of the hot gas duct and at the same time have a particularly small heat input surface. As a result, the vapor content of individual corner tubes of the lower section of the vertical bore can approach zero, so that an unevenly distributed water-vapor mixture enters the intermediate header here. Since the interim 1er also does not cause sufficient mixing here, the mass flow in the downstream corner pipes can come to a standstill and the heat dissipation thus be insufficient. Especially in the case of such a steam generator, therefore, teilhafterweise the downstream of the flow collector steam generator tubes on a throttle device.
Der Durchgangssammler kann durchgängig horizontal umlaufend angeordnet sein, d. h., er verbindet sämtliche unterhalb be¬ ziehungsweise oberhalb angeordneten Dampferzeugerrohre der Umfassungswand miteinander. Trotz des vollständigen Druckausgleichs über alle Rohre können dennoch Entmischungen von Wasser- und Dampfanteil auftreten. Vorteilhafterweise weist da- her auch ein derartiger Zwangdurchlaufdampferzeuger in den dem Durchgangssammler nachgeschalteten Dampferzeugerrohren jeweils eine Drosseleinrichtung auf. The passage collector may be continuous circumferentially arranged horizontally, that is, it connects all be below ¬ relationship as above arranged steam generator tubes of the surrounding wall with each other. Despite the complete pressure equalization over all pipes, segregation of water and steam can still occur. Accordingly, such a forced-circulation steam generator also advantageously has a throttle device in each of the steam generator tubes connected downstream of the through-flow collector.
Die Berohrung unterhalb des Durchgangssammlers kann spiral- förmig umlaufend ausgestaltet sein. Die Rohre verlaufen dabei umlaufend um die gesamte Umfassungswand. Zwar bedingt dies eine komplexere Konstruktion und auch eine geringere Anzahl von Dampferzeugerrohren im unteren Bereich, allerdings werden dadurch Beheizungsunterschiede in verschiedenen Bereichen der Umfassungswand weitgehend ausgeglichen. Dennoch wurde er¬ kannt, dass es auch bei einer derartigen Konstruktion im Durchgangssammler zu zufälligen lokalen Entmischungen kommen kann, die die oben beschriebenen Probleme des zu geringen Massenstroms in den dem Durchgangssammler nachgeschalteten Rohren verursachen. Daher weisen auch bei einer derartigen Konstruktion vorteilhafterweise die dem Durchgangssammler nachgeschalteten Dampferzeugerrohre jeweils eine Drosselein¬ richtung auf. Bei fossil befeuerten Dampferzeugern erfolgt der Wärmeeintrag in die Dampferzeugerrohre der Brennkammer nicht ausschlie߬ lich konvektiv, sondern ein Großteil des Wärmeanteils wird durch Wärmestrahlung in die Dampferzeugerrohre eingebracht. Insbesondere bei derartigen Dampferzeugern können daher die Unterschiede in der Beheizung einzelner Dampferzeugerrohre besonders groß sein. Daher weist vorteilhafterweise ein The tubing below the passage collector can be configured in a spiral shape. The tubes run circumferentially around the entire enclosure wall. Although this causes a more complex construction and also a smaller number of steam generator tubes in the lower area, but this heating differences in various areas of the enclosure wall are largely compensated. Nevertheless, he was ¬ known that even with such a construction in the through-collector to random local segregation can occur, which cause the above-described problems of too low a mass flow in the pipes downstream of the through-collector. Therefore, even with such a construction, advantageously the steam generator tubes connected downstream of the throughflow collector each have a throttle device. In fossil-fired steam generators, the heat input to the steam generator tubes of the combustion chamber does not occur exclu ¬ Lich convectively but a large part of the heat content is introduced by heat radiation in the steam generator tubes. In particular, in such steam generators, therefore, the differences in the heating of individual steam generator tubes can be particularly large. Therefore advantageously has
Dampferzeuger mit einer eine Anzahl von Brennern für fossilen Brennstoff aufweisenden Brennkammer eine Drosseleinrichtung in den dem Durchgangssammler nachgeschalteten Dampferzeuger- rohren auf. Steam generator with a combustor having a number of fossil fuel burners a throttle device in the steam generator pipes connected downstream of the throughput collector.
In vorteilhafter Ausgestaltung ist dem Zwangdurchlaufdampf- erzeuger eine Dampfturbine beispielsweise zur Stromerzeugung strömungsmediumsseitig nachgeschaltet. Weiterhin weist eine Kraftwerksanlage vorteilhafterweise einen derartigen Dampf¬ erzeuger auf. In an advantageous embodiment, the forced-circulation steam generator is followed by a steam turbine, for example for generating electricity, downstream of the flow medium. Furthermore, a power plant advantageously has such a steam ¬ generator.
Die mit der Erfindung erzielten Vorteile bestehen insbesonde re darin, dass durch die Anordnung einer Drosseleinrichtung in den dem Durchgangssammler nachgeschalteten Dampferzeuger- rohren eines Zwangdurchlaufdampferzeugers ein ausreichender Wärmeabtransport in jedem Rohr gewährleistet ist und somit unzulässig hohe Temperaturen, die zu Beschädigungen der Rohr wand führen können, vermieden werden. Dabei beruht diese Maß nähme auf der Erkenntnis, dass auch in einem Zwangdurchlauf- dampferzeuger eine nicht zu vernachlässigende Naturumlaufcha rakteristik vorhanden ist, die durch die Anordnung von Drosseln abgeschwächt wird. Letztlich werden dadurch Einschränkungen im Betrieb einer Kraftwerksanlage vermieden. The advantages achieved by the invention insbesonde re is that the arrangement of a throttle device in the passage collector downstream steam generator tubes a forced flow steam generator sufficient heat dissipation in each tube is guaranteed and thus inadmissible high temperatures that can damage the pipe wall, be avoided. This measure is based on the realization that even in a forced continuous steam generator a non-negligible natural circulation characteristic is present, which is weakened by the arrangement of throttles. Ultimately, this restriction in the operation of a power plant avoided.
Die Erfindung wird anhand einer Zeichnung näher erläutert. Darin zeigen: The invention will be explained in more detail with reference to a drawing. Show:
FIG 1 schematisch einen senkrecht berohrten 1 schematically shows a vertically bored
Zwangdurchlaufdampferzeuger mit Durchgangssammler, und  Forced circulation steam generator with throughput collector, and
FIG 2 eine grafische Darstellung der Massenstromdichte und der Fluidtemperatur am Austritt eines vergleichsweise schwach beheizten Eckrohres des Zwangdurchlaufdampferzeugers mit und ohne Drosseleinrichtung . 2 shows a graphical representation of the mass flow density and the fluid temperature at the outlet of a comparatively weakly heated corner tube of the once-through steam generator with and without throttle device.
Gleiche Teile sind in allen Figuren mit denselben Bezugszei¬ chen versehen. FIG 1 zeigt schematisch einen fossil befeuerten, senkrecht berohrten Zwangdurchlaufdampferzeuger 1 gemäß der Erfindung. Der Zwangdurchlaufdampferzeuger 1 umfasst eine aus gasdicht verschweißten Dampferzeugerrohren 2 gebildete Umfassungswand 4. Die Umfassungswand 4 weist dabei einen im Wesentlichen rechteckigen horizontalen Querschnitt 6 auf. Im unteren Bereich des Zwangdurchlaufdampferzeugers 1 ist eine Brennkammer 8 mit einer Anzahl von nicht näher dargestellten Brennern zur Verbrennung eines fossilen Brennstoffs angeordnet, die die Wärmezufuhr zu den Dampferzeugerrohren 4 bereitstellen. Identical parts are provided in all figures with the same Bezugszei ¬ chen. 1 schematically shows a fossil-fired, vertically bored forced once-through steam generator 1 according to the invention. The once-through steam generator 1 comprises an enclosing wall 4 formed from gas-tightly welded steam generator tubes 2. The enclosing wall 4 has a substantially rectangular horizontal cross-section 6. In the lower region of the once-through steam generator 1, a combustion chamber 8 is arranged with a number of burners not shown in detail for the combustion of a fossil fuel, which provide the heat supply to the steam generator tubes 4.
Die Umfassungswand 4 ist in einen oberen Abschnitt 10 und ei¬ nen unteren Abschnitt 12 unterteilt, wobei die Abschnitte 10 und 12 über einen Durchgangssammler 14 miteinander verbunden sind. Die Berohrung im unteren Abschnitt 12 ist hier senkrecht angeordnet, kann aber auch spiralförmig um die Umfassungswand umlaufend angeordnet sein. Der Durchgangssammler 14 sammelt das gesamte aus den Dampferzeugerrohren 2 des unteren Abschnitts 12 austretende Strömungsmedium und ermöglicht so einen Druckausgleich zwischen den parallel geschalteten The enclosure wall 4 is divided into an upper portion 10 and ei ¬ NEN lower portion 12, wherein the portions 10 and 12 are connected to each other via a through-collector 14. The tubing in the lower portion 12 is arranged vertically here, but may also be arranged spirally around the Umfassungswand circumferentially. The passage collector 14 collects all of the flow medium exiting from the steam generator tubes 2 of the lower section 12 and thus enables a pressure equalization between the parallel connected
Dampferzeugerrohren 2. Anschließend wird das Strömungsmedium aus dem Durchgangssammler 14 in die Dampferzeugerrohre 2 des oberen Abschnitts 10 eingeleitet, wo es weiter erwärmt und gegebenenfalls überhitzt wird. Der überhitzte Dampf wird nach weiterer Überhitzung in nicht dargestellten Heizflächen einer nicht näher dargestellten Dampfturbine in einer Kraftwerks¬ anlage zugeführt. Steam generator tubes 2. Subsequently, the flow medium from the passage collector 14 is introduced into the steam generator tubes 2 of the upper portion 10, where it is further heated and optionally superheated. The superheated steam is supplied after further overheating in not shown heating surfaces of a steam turbine not shown in a power plant ¬ system.
Die durch die Brenner erzeugte Wärme wird weitestgehend über Wärmestrahlung durch die Dampferzeugerrohre 2 aufgenommen. Insbesondere in den Eckrohren 16 des unteren Abschnitts 12 ist aufgrund ihrer Lage in der größten Entfernung zum Zentrum des Zwangdurchlaufdampferzeugers 1 und aufgrund der geometri¬ schen Anordnung der besonders gering mit Wärme beaufschlagten Oberfläche der Wärmeeintrag so gering, dass das aus den Eck¬ rohren 16 des unteren Abschnitts 12 in den Durchgangssammler 14 eintretende Strömungsmedium einen vergleichsweise geringen Dampfgehalt aufweist. Der Durchgangssammler 14 bewirkt nun zwar einen vollständigen Druckausgleich, jedoch keine vollständige Durchmischung des eintretenden Strömungsmediums. Aufgrund des beschriebenen niedrigen Dampfgehalts am Austritt aus den Eckrohren 16 des unteren Abschnitts 12 sowie zusätzlicher lokaler Entmischungsphänomene im Durchgangssammler 14 kann der Dampfgehalt am Eintritt in einzelne Dampferzeugerrohre 2 des oberen Abschnitts 10 sehr gering werden. Je nach Betriebszustand des Zwangdurchlaufdampferzeugers 1 kann dies bei einer unvorteil¬ haften Auslegung der Berohrung des oberen Abschnitts 10 zu einem deutlichen Einbruch der Durchströmung einzelner Dampferzeugerrohre 2 bis hin zur Stagnation führen. Dies wiederum kann einen unzureichenden Wärmeabtransport und unzulässig hohe Fluidtemperaturen zur Folge haben, so dass letztlich die Rohrwand unzulässig hohe Temperaturen annimmt und zerstört wird . The heat generated by the burner is largely absorbed by heat radiation through the steam generator tubes 2. Particularly in the corner tubes 16 of the lower portion 12 of the geometric ¬ rule arrangement of particularly low applied with heat surface of the heat input due to its location at the greatest distance to the center of the once-through steam generator 1, and due to so low that the from the corner ¬ tubes 16 of the lower portion 12 in the passage header 14 entering flow medium has a comparatively low vapor content. Although the passage collector 14 now effects a complete pressure equalization, however, no complete mixing of the incoming flow medium. Due to the described low vapor content at the exit from the corner tubes 16 of the lower section 12 as well as additional local segregation phenomena in the passage header 14, the vapor content at the entrance to individual steam generator tubes 2 of the upper section 10 can become very small. Depending on the operating state of the once-through steam generator 1 which may cause a misinterpretation unvorteil ¬ the tubing of the upper portion 10 to a significant drop of the flow through individual steam generator tubes 2 through to stagnation. This in turn can result in insufficient heat removal and inadmissibly high fluid temperatures, so that ultimately the pipe wall assumes inadmissibly high temperatures and is destroyed.
Zur Vermeidung einer derartigen Beschädigung sind im Ausfüh- rungsbeispiel am Austritt sämtlicher Dampferzeugerrohre des oberen Bereichs 10 Drosseleinrichtungen 18 angeordnet, wobei zur einfacheren Darstellung beispielhaft nur einzelne Drosseleinrichtungen 18 gezeigt sind. Die Drosseleinrichtungen 18 sind jeweils als Blende ausgestaltet, wodurch der Gesamt- druckverlust für alle parallelen Rohre erhöht wird. Dies führt dazu, dass der hydrostatische Druckabfall in den jewei¬ ligen Dampferzeugerrohren 2, insbesondere in den Eckrohren 16 relativ gesehen reduziert wird. Somit bleibt stets eine aus¬ reichende Druckdifferenz als treibende Kraft der Strömung vorhanden. Dieser Effekt wird anhand der FIG 2 verdeutlicht: In order to avoid such damage, throttling devices 18 are arranged in the exemplary embodiment at the outlet of all the steam generator tubes of the upper region 10, with only individual throttle devices 18 being shown by way of example in order to simplify the illustration. The throttle devices 18 are each designed as a diaphragm, whereby the total pressure loss is increased for all parallel tubes. This results in that the hydrostatic pressure drop in the jewei ¬ then steam generator tubes 2, in particular in the corner tubes 16 is reduced in relative terms. Thus, a reaching out ¬ pressure difference always remains available as a driving force of the flow. This effect is illustrated by FIG. 2:
FIG 2 zeigt eine grafische Darstellung der Parameter des Strömungsmediums in einem Eckrohr 16 des oberen Bereichs 10 mit und ohne Drosseleinrichtung 18 bei vergleichsweise gerin- ger Wärmezufuhr und für einen Teillastbetrieb des Dampferzeu¬ gers 1. Die linke Skala zeigt die Massenstromdichte im Eck¬ rohr 16 in Kilogramm pro Quadratmeter und Sekunde (kg/m2s) , in die rechte Skala zeigt die Fluidtemperatur am Austritt des Eckrohres 16 in Grad Celsius (°C), jeweils aufgetragen gegen den Dampfanteil des Strömungsmediums am Rohreintritt. 2 shows a graphical representation of the parameters of the flow medium in a corner pipe 16 of the upper portion 10 with and without throttle device 18 at comparatively low ger supply of heat and for a partial load operation of Dampferzeu ¬ gers 1. The left-hand scale shows the mass flow density in the corner ¬ pipe 16 in kilograms per square meter and second (kg / m2s), in the right scale shows the fluid temperature at the outlet of the Corner tube 16 in degrees Celsius (° C), each plotted against the vapor content of the flow medium at the tube inlet.
Kurvenzug 20 zeigt die Massenstromdichte im Eckrohr 16 ohne gesonderte Drosseleinrichtung 18. Der Abfall des Kurvenzugs 20 zur linken Seite der grafischen Darstellung zeigt deutlich, wie hin zu geringeren Dampfanfeilen die Massenstrom- dichte im Eckrohr 16 abnimmt. Bei einem Dampfanteil von 0 sinkt die Massenstromdichte auf einen Wert von 40 kg/m2s ab, was praktisch einer Stagnation der Strömung im Rohr gleichkommt. Ein ausreichender Wärmeabtransport im Rohr ist nicht mehr gewährleistet und entsprechend steigt die Temperatur des Strömungsmediums und damit des Eckrohres 16 ab einem Dampfan¬ teil von etwa 0,2 signifikant an, wie Kurvenzug 22 darstellt. Curve 20 shows the mass flow density in the corner tube 16 without a separate throttle device 18. The drop of the curve 20 to the left of the graph clearly shows how toward lower Dampfanfeilen the mass flow density in the corner tube 16 decreases. With a vapor content of 0, the mass flow density drops to a value of 40 kg / m2s, which practically equates to a stagnation of the flow in the pipe. A sufficient heat dissipation in the pipe is no longer guaranteed and accordingly increases the temperature of the flow medium and thus of the corner tube 16 from a Dampfan ¬ part of about 0.2 significantly, as curve 22 represents.
Bei Anordnung einer Drosseleinrichtung 18 im Eckrohr 16 an dessen Austritt erhöht sich jedoch der Reibungsdruckverlust und reduziert damit wie oben beschrieben die NaturumlaufCha¬ rakteristik und vermindert so einen übermäßigen relativen hydrostatischen Druckabfall im Eckrohr 16. Kurvenzug 24 zeigt zwar auch, dass hin zu niedrigeren Dampfgehalten die Massenstromdichte in Eckrohr 16 abnimmt. Dabei bleibt aber der Wert der Massenstromdichte auch bei einem Dampfanteil von 0 auf einem wesentlich höheren Wert (hier 260 kg/m2s) als in einer Anordnung ohne Drosseleinrichtung 18. Wie Kurvenzug 26 verdeutlicht, führt dies dazu, dass bei jedwedem Dampfgehalt ein ausreichender Wärmeabtransport im Eckrohr 16 gewährleistet ist, d. h., die Temperatur nur in geringem Maße ansteigt oder konstant bleibt. Dadurch werden Beschädigungen der Umfas- sungswand 4 im oberen Bereich 10 durch übermäßige Temperatu¬ ren vermieden und es wird eine insgesamt höhere Lebensdauer des Zwangdurchlaufdampferzeugers 1 erreicht. However, the arrangement of a throttle device 18 in the corner tube 16 at the outlet increases the friction pressure loss and thus reduces the NaturumlaufCha ¬ characteristic as described above and thus reduces excessive relative hydrostatic pressure drop in the corner tube 16. Curve 24 also shows that toward lower vapor levels the Mass flow density in the corner tube 16 decreases. However, the value of the mass flow density remains at a vapor content of 0 at a much higher value (here 260 kg / m2s) than in an arrangement without throttle device 18. As curve 26 illustrates, this means that at any steam content sufficient heat dissipation in Corner tube 16 is ensured, that is, the temperature increases only slightly or remains constant. Damage to the Umfas- sungswand 4 in the upper region 10 by excessive Temperatu ¬ ren avoided and it is an overall longer life of the forced once-through steam generator 1 achieved.

Claims

Patentansprüche claims
1. Zwangdurchlaufdampferzeuger (1) mit einer aus gasdicht verschweißten, in vertikaler Richtung durchströmbaren Dampf- erzeugerrohren (2) gebildeten Umfassungswand (4), bei dem innerhalb der Umfassungswand (4) ein Durchgangssammler (14) angeordnet ist, der eine erste Mehrzahl parallel geschalteter Dampferzeugerrohre (2) austrittsseitig mit einer zweiten, der ersten Mehrzahl seriell nachgeschalteten Mehrzahl parallel geschalteter Dampferzeugerrohre (2) eintrittsseitig strö- mungsmediumsseitig verbindet, wobei die dem Durchgangssammler (14) nachgeschalteten Dampferzeugerrohre (2) jeweils eine Drosseleinrichtung (18) aufweisen. 1. Continuous flow steam generator (1) with a welded gas-tight welded, in the vertical direction steam generator tubes (2) formed Umfassungswand (4), wherein within the Umfassungswand (4) a passage collector (14) is arranged, the first plurality of parallel connected Steam generator tubes (2) on the outlet side with a second, the first plurality serially downstream plurality of parallel connected steam generator tubes (2) on the inlet side flow medium side connects, wherein the passage collector (14) downstream steam generator tubes (2) each have a throttle device (18).
2. Zwangdurchlaufdampferzeuger (1) nach Anspruch 1, bei dem die jeweilige Drosseleinrichtung (18) am oberen Austritt der Umfassungswand (4) angeordnet ist. 2. forced once-through steam generator (1) according to claim 1, wherein the respective throttle device (18) at the upper outlet of the surrounding wall (4) is arranged.
3. Zwangdurchlaufdampferzeuger (1) nach einem der vorherge- henden Ansprüche, bei dem die Drosseleinrichtung (18) als3. forced continuous steam generator (1) according to one of the preceding claims, wherein the throttle device (18) as
Blende ausgestaltet ist. Aperture is designed.
4. Zwangdurchlaufdampferzeuger (1) nach einem der vorhergehenden Ansprüche, bei dem die Umfassungswand (4) einen im We- sentlichen rechteckigen horizontalen Querschnitt (6) aufweist. 4. forced once-through steam generator (1) according to one of the preceding claims, wherein the peripheral wall (4) has a substantially rectangular horizontal cross-section (6).
5. Zwangdurchlaufdampferzeuger (1) nach einem der vorhergehenden Ansprüche, bei dem der Durchgangssammler (14) horizon- tal um die Umfassungswand (4) umlaufend angeordnet ist und die erste Mehrzahl sämtliche unterhalb in der Umfassungswand (4) angeordneten, parallel geschalteten Dampferzeugerrohre (2) umfasst und die zweite Mehrzahl sämtliche oberhalb in der Umfassungswand (4) angeordneten Dampferzeugerrohre (2) um- fasst. 5. forced once-through steam generator (1) according to one of the preceding claims, wherein the passage collector (14) horizontally around the Umfassungswand (4) is arranged circumferentially and the first plurality all below in the enclosure wall (4) arranged in parallel steam generator tubes (2 ) and the second plurality comprises all above in the enclosure wall (4) arranged steam generator tubes (2).
6. Zwangdurchlaufdampferzeuger nach einem der 6. forced once-through steam generator according to one of
vorhergehenden Ansprüche, bei dem die dem Durchgangssammler (14) vorgeschalteten Dampferzeugerrohre (2) spiralförmig umlaufend in der Umfassungswand (4) angeordnet sind. preceding claims, wherein the passage collector (14) upstream steam generator tubes (2) are arranged spirally encircling in the enclosure wall (4).
7. Zwangdurchlaufdampferzeuger (1) nach einem der vorherge henden Ansprüche mit einer eine Anzahl von Brennern für fossilen Brennstoff aufweisenden Brennkammer (8). 7. forced once-through steam generator (1) according to one of vorherge existing claims with a number of burners for fossil fuel having combustion chamber (8).
8. Zwangdurchlaufdampferzeuger (1) nach einem der vorherge henden Ansprüche mit einer strömungsmediumsseitig nachge¬ schalteten Dampfturbine. 8. forced once-through steam generator (1) according to one of vorherge existing claims with a downstream side ¬ switched steam turbine.
9. Kraftwerksanlage mit einem Zwangdurchlaufdampferzeuger (1) nach einem der vorhergehenden Ansprüche. 9. power plant with a forced once-through steam generator (1) according to one of the preceding claims.
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WO2012016749A3 (en) 2013-02-07
AU2011287835A1 (en) 2013-02-21
US20130205784A1 (en) 2013-08-15
DE102010038883C5 (en) 2021-05-20
WO2012016749A2 (en) 2012-02-09
DE102010038883B4 (en) 2017-05-24
EP2601441B1 (en) 2016-08-17
AU2011287835B2 (en) 2014-03-20
DE102010038883A1 (en) 2012-02-09
CN103154611A (en) 2013-06-12
KR20140003372A (en) 2014-01-09
CN103154611B (en) 2016-03-16
US9291344B2 (en) 2016-03-22

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