WO2012028494A2 - Solar thermal continuous evaporator heating surface with local cross-sectional narrowing on the inlet thereof - Google Patents
Solar thermal continuous evaporator heating surface with local cross-sectional narrowing on the inlet thereof Download PDFInfo
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- WO2012028494A2 WO2012028494A2 PCT/EP2011/064457 EP2011064457W WO2012028494A2 WO 2012028494 A2 WO2012028494 A2 WO 2012028494A2 EP 2011064457 W EP2011064457 W EP 2011064457W WO 2012028494 A2 WO2012028494 A2 WO 2012028494A2
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- Prior art keywords
- steam generator
- heating surface
- solar
- solar thermal
- inlet
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/006—Methods of steam generation characterised by form of heating method using solar heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B29/00—Steam boilers of forced-flow type
- F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
- F22B29/061—Construction of tube walls
- F22B29/062—Construction of tube walls involving vertically-disposed water tubes
-
- 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
- F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
- F22B37/10—Water tubes; Accessories therefor
- F22B37/12—Forms of water tubes, e.g. of varying cross-section
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
- F24S10/00—Solar heat collectors using working fluids
- F24S10/70—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits
- F24S10/74—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits the tubular conduits are not fixed to heat absorbing plates and are not touching each other
- F24S10/742—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits the tubular conduits are not fixed to heat absorbing plates and are not touching each other the conduits being parallel to each other
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
- F24S20/00—Solar heat collectors specially adapted for particular uses or environments
- F24S20/20—Solar heat collectors for receiving concentrated solar energy, e.g. receivers for solar power plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
- F24S80/00—Details, accessories or component parts of solar heat collectors not provided for in groups F24S10/00-F24S70/00
- F24S2080/03—Arrangements for heat transfer optimization
- F24S2080/05—Flow guiding means; Inserts inside conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
- F24S23/00—Arrangements for concentrating solar-rays for solar heat collectors
- F24S23/70—Arrangements for concentrating solar-rays for solar heat collectors with reflectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
- F24S80/00—Details, accessories or component parts of solar heat collectors not provided for in groups F24S10/00-F24S70/00
- F24S80/30—Arrangements for connecting the fluid circuits of solar collectors with each other or with other components, e.g. pipe connections; Fluid distributing means, e.g. headers
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/40—Solar thermal energy, e.g. solar towers
- Y02E10/44—Heat exchange systems
Definitions
- the invention relates to a solar thermal through ⁇ evaporator heating surface, in particular for a solar tower power plant, comprising an absorber with steam generator tubes.
- the invention further relates to a solar tower power plant with a solar thermal continuous evaporator heating surface.
- Solar thermal power plants are therefore one of the sustainable alternatives to conventional power generation. So far, solar thermal power plants have been designed with parabolic trough collectors or Fresnel collectors. Another option is the direct evaporation in so-called solar tower power plants.
- a solar thermal power plant with a solar tower and direct expansion consists of a solar array, a solar tower and of a conventional power plant part in which converting the thermal energy of the water vapor in electrical ⁇ specific energy becomes.
- the solar field consists of heliostats that focus the Clarstrah ⁇ Assembly at one housed in the solar tower absorbers.
- the absorber consists of a heating surface in which the irradiated solar energy is used to heat supplied feed water, to evaporate and possibly also to overheat.
- the generated steam is then expanded in a conventional power plant part in a turbine, optionally reheated and then condensed and fed back to the absorber.
- the turbine drives a generator, which converts the mechanical energy into electrical energy.
- the solar energy introduced is limited by the size of the heliostat field. Part of the radiation is reflected by the absorber and is lost to the thermodynamic power plant process. These losses increase with the size of the heating surface. Therefore, for a given thermal performance compact absorbers with the smallest possible heating surface are desirable. This leads by concentrating the scattered solar energy on small areas to very high heat flux densities, generally higher ren heat flux densities than in fossil-fired thermal power plants. Therefore, with the concept of direct evaporation in a solar tower power plant, the cooling of the absorber heating surface is of central importance. In order to minimize the size of the heating surface, conditions must be set to the highest possible heat flow densities. The upper limit of the permissible heat flow densities is determined by the pipe material and by the quality of the cooling mechanisms.
- continuous steam generators are not subject to any pressure limitation, s that live steam pressures far above the critical pressure of water are possible. This high live steam pressure promotes a high thermodynamic efficiency of a power plant.
- the invention is thus based on the object to provide a solar thermal ⁇ flow evaporator heating surface for a solar thermal ⁇ pass evaporator, in particular in a solar tower power plant for the highest possible heat flow. Furthermore, a correspondingly improved solar tower power plant with high thermodynamic efficiency should be specified.
- the invention is based on the recognition that the pressure loss of the two-phase flow or steam path acts as a throttle at the outlet of the system and is destabilizing.
- the relative proportion of this pressure ⁇ loss of total pressure loss of the system is to minimize the occurring defects ⁇ th instability.
- the pressure loss component in the inlet region of the steam generator ie in the single-phase region of the water flow, is increased. With proper positioning and dimensioning of the cross-sectional constriction so instabilities can be safely avoided.
- a throttle is arranged as a local cross-sectional constrictions in at least ei ⁇ nem steam generator tube.
- a nipple arranged between inlet collector and steam generator tube has a smaller inner diameter than the at least one steam generator tube.
- a collector at the inlet is smaller Austritts tellmes ⁇ ser, than an inner diameter of at least a steam generator tube.
- the solar thermal continuous evaporator heating surface is integrated according to a particularly advantageous embodiment in a solar tower power plant and directly for steam generation by focused solar radiation acted upon.
- FIG. 5 shows an inlet collector with steam generator tubes, which are connected via nipples to the inlet header and 6 shows an inlet header with steam generator tubes, wherein outlet diameters at the inlet header are smaller than the inside diameter of the steam generator tubes.
- FIG. 1 shows the solar part of a solar tower power plant 1.
- the solar tower power plant 1 comprises a solar tower 2, at whose vertical upper end an absorber 3 is arranged.
- a heliostat field 4 with a number of heliostats 5 is placed on the ground around the solar tower 2.
- the heliostat 4 with the heliostat 5 is designed for focusing the direct solar radiation 6.
- the individual suspenders 5 are arranged and aligned such that the direct solar radiation 6 is focused by the sun in the form of concentrated solar radiation 7 onto the absorber 3.
- the solar radiation is thus concentrated on the tip of the solar tower 2 by a field of individually tracked mirrors, the heliostats 5.
- the absorber 3 converts the radiation into heat, and outputs it to a heat ⁇ carrier medium, for example water, from which with a steam turbine, the heat leads to a conventional power plant process to ⁇ .
- an evaporator 8 is of a known so ⁇ larthermischen forced circulation steam generator 9 shown with direct evaporation, which is integrated as an absorber 3 in the solar tower 2 of Fig. 1
- the steam generator tubes 10 on the input side a ⁇ occurs collector 11 and its output connected to a manifold 12 with an outlet fluidically.
- Overflow pipes 13 connect the outlet header 12 with a drum 14, into which a feedwater line 15 opens.
- a feedwater pump 16 is connected.
- the downpipe 18 opens into the inlet header 11.
- the pump In operation of the solar-heated forced-circulation steam generator 9, the pump sucks water from the boiler 19 to the drum 14 and presses it into the inlet header 11. There, the Kes ⁇ selwasser is distributed to the plurality of heat-transferring steam generator tubes 10th The evaporator 8 is divided into parallel ⁇ Bank inhabitrohre. The heat-transferring tubes 10 are heated by the concentrated solar radiation 7, wherein the heat-transferring tubes 10 deliver the heat to the boiler water. The resulting
- FIG 3 shows the principle of a solar thermal once-through steam generator 21, in which the passage of the water-steam stream is forced by the fürvierdampferHeiz Structure 20 of a feedwater pump sixteenth
- the feed water is conveyed by the feed water pump 16 into the inlet header 11 and the evaporator inlet 22, and the steam generator tubes 10 of the continuous evaporator heating surface 20 and the superheater 23 are flowed through successively (in the case of solar thermal power plants, a feedwater pre-heater is typically omitted).
- a separating device 24 is provided for circulation when the system starts up.
- FIG. 4 shows a preferred embodiment of a local cross-sectional constriction built into a steam generator tube 10 of the continuous evaporator heating surface 20 of the continuous-flow steam generator 21, designed as a throttle 25.
- a throttle 25 is connected in the evaporator inlet 22 of each steam generator tube 10 of the continuous evaporator heating surface 20.
- the preheated feed water flows via the Dros ⁇ nel 25 into the individual steam generator tubes 10 of the solar thermal continuous evaporator heating surface 20th ,
- the throttles 25 ensure virtually over the entire load range of the solar thermal continuous steam generator 21 an increased pressure drop in the evaporator. In this case, a stable and uniform flow of the preheated feed water through the steam generator tubes 10 is achieved.
- FIG. 5 shows an alternative cross-sectional constriction, which is as ⁇ achieved by that between the inlet header 11 and Steam generator tubes 10 arranged nipple 26 have a smaller inner diameter than the steam generator tubes 10.
- FIG. 6 shows a further embodiment of the local cross-sectional constriction, which results from the fact that outlet diameters 27 at the inlet header 11 are smaller than the inside diameter 28 of the steam generator tubes 10.
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- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
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Abstract
Description
Beschreibung description
Solarthermische Durchlaufverdampfer-Heizfläche mit lokaler Querschnittsverengung an ihrem Eintritt Solar thermal continuous evaporator heating surface with local cross-sectional constriction at its inlet
Die Erfindung bezieht sich auf eine solarthermische Durch¬ laufverdampfer-Heizfläche, insbesondere für ein Solarturm- Kraftwerk, umfassend einen Absorber mit Dampferzeugerrohren . Die Erfindung betrifft weiterhin ein Solarturm-Kraftwerk mit einer solarthermischen Durchlaufverdampfer-Heizfläche. The invention relates to a solar thermal through ¬ evaporator heating surface, in particular for a solar tower power plant, comprising an absorber with steam generator tubes. The invention further relates to a solar tower power plant with a solar thermal continuous evaporator heating surface.
Dem stetig steigenden Energiebedarf und dem Klimawandel muss mit dem Einsatz von nachhaltigen Energieträgern entgegengetreten werden. Sonnenenergie ist solch ein nachhaltiger Ener- gieträger. Sie ist klimaschonend, in unerschöpflichem Maße vorhanden und stellt keine Belastung für nachkommende Genera¬ tionen dar. The steadily rising energy demand and climate change must be tackled with the use of sustainable energy sources. Solar energy is such a sustainable energy source. It is climate-friendly, yet inexhaustibly and is not a burden for is a descendant genera ¬ tions.
Solarthermische Kraftwerke stellen deshalb eine der nachhal- tigen Alternativen zur herkömmlichen Stromerzeugung dar. Bisher wurden solarthermische Kraftwerke mit Parabolrinnenkol- lektoren oder Fresnel-Kollektoren ausgeführt. Eine weitere Option stellt die direkte Verdampfung in sogenannten Solarturm-Kraftwerken dar. Ein solarthermisches Kraftwerk mit So- larturm und direkter Verdampfung besteht aus einem Solarfeld, einem Solarturm und aus einem konventionellen Kraftwerksteil, in dem die thermische Energie des Wasserdampfes in elektri¬ sche Energie umgewandelt wird. Das Solarfeld besteht aus Heliostaten, die die Sonnenstrah¬ lung auf einen im Solarturm untergebrachten Absorber konzentrieren. Der Absorber besteht aus einer Heizfläche, in der die eingestrahlte Sonnenenergie dazu genutzt wird, um zugeführtes Speisewasser zu erwärmen, zu verdampfen und gegebenenfalls auch zu überhitzen. Der erzeugte Dampf wird anschließend in einem konventionellen Kraftwerkssteil in einer Turbine entspannt, gegebenenfalls zwischenüberhitzt und anschließend kondensiert und dem Absorber wieder zugeführt. Die Turbine treibt einen Generator an, der die mechanische Energie in elektrische Energie wandelt. Solar thermal power plants are therefore one of the sustainable alternatives to conventional power generation. So far, solar thermal power plants have been designed with parabolic trough collectors or Fresnel collectors. Another option is the direct evaporation in so-called solar tower power plants. A solar thermal power plant with a solar tower and direct expansion consists of a solar array, a solar tower and of a conventional power plant part in which converting the thermal energy of the water vapor in electrical ¬ specific energy becomes. The solar field consists of heliostats that focus the Sonnenstrah ¬ Assembly at one housed in the solar tower absorbers. The absorber consists of a heating surface in which the irradiated solar energy is used to heat supplied feed water, to evaporate and possibly also to overheat. The generated steam is then expanded in a conventional power plant part in a turbine, optionally reheated and then condensed and fed back to the absorber. The turbine drives a generator, which converts the mechanical energy into electrical energy.
In einem Solarturm-Kraftwerk ist die eingebrachte Sonnenener gie durch die Größe des Heliostatenfeldes begrenzt. Ein Teil der Einstrahlung wird vom Absorber reflektiert und ist für den thermodynamischen Kraftwerkprozess verloren. Diese Verluste wachsen mit der Größe der Heizfläche. Deshalb sind bei gegebener thermischer Leistung kompakte Absorber mit möglichst kleiner Heizfläche anzustreben. Dies führt durch die Konzentrierung der eingestreuten Sonnenenergie auf kleine Flächen zu sehr hohen Wärmestromdichten, im allgemeinen höhe ren Wärmestromdichten als in fossil befeuerten thermischen Kraftwerken. Deshalb ist bei dem Konzept der Direktverdampfung in einem Solarturm-Kraftwerk die Kühlung der Absorberheizfläche von zentraler Bedeutung. Zur Minimierung der Heiz flächengröße ist auf größtmögliche Wärmestromdichten auszule gen. Die Obergrenze der zulässigen Wärmestromdichten wird durch das Rohrmaterial und durch die Qualität der Kühlungsme chanismen bestimmt. In a solar tower power plant, the solar energy introduced is limited by the size of the heliostat field. Part of the radiation is reflected by the absorber and is lost to the thermodynamic power plant process. These losses increase with the size of the heating surface. Therefore, for a given thermal performance compact absorbers with the smallest possible heating surface are desirable. This leads by concentrating the scattered solar energy on small areas to very high heat flux densities, generally higher ren heat flux densities than in fossil-fired thermal power plants. Therefore, with the concept of direct evaporation in a solar tower power plant, the cooling of the absorber heating surface is of central importance. In order to minimize the size of the heating surface, conditions must be set to the highest possible heat flow densities. The upper limit of the permissible heat flow densities is determined by the pipe material and by the quality of the cooling mechanisms.
Im Gegensatz zu einem Natur- oder Zwangumlaufdampferzeuger unterliegen Durchlaufdampferzeuger keiner Druckbegrenzung, s dass Frischdampfdrücke weit über dem kritischen Druck von Wasser möglich sind. Dieser hohe Frischdampfdruck begünstigt einen hohen thermodynamischen Wirkungsgrad eines Kraftwerks. In contrast to a natural or forced circulation steam generator, continuous steam generators are not subject to any pressure limitation, s that live steam pressures far above the critical pressure of water are possible. This high live steam pressure promotes a high thermodynamic efficiency of a power plant.
In Durchlaufverdampfer-Heizflächen können statische und dyna mische Instabilitäten auftreten, die in konventionellen Kraftwerken in der Vergangenheit zu Schäden geführt haben. Dieses Risiko ist aufgrund der hohen Energiedichte bei solar thermischen Anlagen erhöht. In continuous evaporator heating surfaces static and dynamic instabilities can occur, which have led to damage in conventional power plants in the past. This risk is increased due to the high energy density of solar thermal systems.
Es besteht daher insbesondere bei solarthermischen Kraft¬ werksanlagen die Notwendigkeit, Instabilitäten in der Verdampferheizfläche des Absorbers zu vermeiden. Der Erfindung liegt somit die Aufgabe zugrunde, eine solar¬ thermische Durchlaufverdampfer-Heizfläche für einen solar¬ thermischen Durchlaufverdampfer insbesondere in einem Solarturm-Kraftwerk für höchstmöglichen Wärmestrom anzugeben. Des Weiteren soll ein entsprechend verbessertes Solarturm- Kraftwerk mit hohem thermodynamischem Wirkungsgrad angegeben werden . It is therefore particularly in solar thermal power plant facilities ¬ the need to avoid instabilities in the evaporator of the absorber. The invention is thus based on the object to provide a solar thermal ¬ flow evaporator heating surface for a solar thermal ¬ pass evaporator, in particular in a solar tower power plant for the highest possible heat flow. Furthermore, a correspondingly improved solar tower power plant with high thermodynamic efficiency should be specified.
Die auf eine solarthermische Durchlaufverdampfer-Heizfläche gerichtete Aufgabe wird erfindungsgemäß gelöst durch die An¬ gabe einer solarthermischen Durchlaufverdampfer-Heizfläche, insbesondere für ein Solarturm-Kraftwerk, umfassend einen Ab sorber mit Dampferzeugerrohren, wobei mindestens ein Dampfer zeugerrohr an seinem Eintritt jeweils eine lokale Quer¬ schnittsverengung aufweist. Which relates to a solar thermal flow evaporator heating surface object is solved by the on ¬ administration of a solar thermal flow evaporator heating surface, in particular for a solar tower power plant comprising a rate from sorber steam generator tubes, wherein at least a steamer zeugerrohr at its entrance in each case a local cross ¬ has narrowing.
Hinsichtlich der lokalen Querschnittsverengung am Eintritt der Dampferzeugerrohre geht die Erfindung von der Erkenntnis aus, dass der Druckverlust der Zweiphasenströmung bzw. der Dampfstrecke wie eine Drossel am Austritt des Systems wirkt und destabilisierend ist. Der relative Anteil dieses Druck¬ verlustes am Gesamtdruckverlust des Systems ist beim Auftre¬ ten einer Instabilität zu minimieren. Durch die vorgeschlage ne Maßnahme wird der Druckverlustanteil im Eintrittsbereich des Dampferzeugers, d.h. im einphasigen Bereich der Wasserströmung, erhöht. Bei richtiger Positionierung und Dimensionierung der Querschnittsverengung können so Instabilitäten sicher vermieden werden. With regard to the local cross-sectional constriction at the entrance of the steam generator tubes, the invention is based on the recognition that the pressure loss of the two-phase flow or steam path acts as a throttle at the outlet of the system and is destabilizing. The relative proportion of this pressure ¬ loss of total pressure loss of the system is to minimize the occurring defects ¬ th instability. By the proposed measure, the pressure loss component in the inlet region of the steam generator, ie in the single-phase region of the water flow, is increased. With proper positioning and dimensioning of the cross-sectional constriction so instabilities can be safely avoided.
In einer vorteilhaften Ausgestaltung der Erfindung ist eine Drossel als lokale Querschnittsverengungen in mindestens ei¬ nem Dampferzeugerrohr angeordnet. In an advantageous embodiment of the invention, a throttle is arranged as a local cross-sectional constrictions in at least ei ¬ nem steam generator tube.
In einer weiteren vorteilhaften Ausgestaltung weist ein zwischen Eintrittssammler und Dampferzeugerrohr angeordneter Nippel einen kleineren Innendurchmesser als das mindestens eine Dampferzeugerrohr auf. Ebenso vorteilhaft kann es sein, wenn ein Austrittsdurchmes¬ ser am Eintrittssammler kleiner ist, als ein Innendurchmesser des mindestens einen Dampferzeugerrohrs . Üblicherweise um- fasst die Durchlaufverdampfer-Heizfläche mehrere Dampferzeu¬ gerrohre, wobei es dann vorteilhaft ist, wenn die Austritts¬ durchmesser am Eintrittssammler kleiner sind, als die Innendurchmesser der Dampferzeugerrohre . In a further advantageous embodiment, a nipple arranged between inlet collector and steam generator tube has a smaller inner diameter than the at least one steam generator tube. Likewise, it may be advantageous if a collector at the inlet is smaller Austrittsdurchmes ¬ ser, than an inner diameter of at least a steam generator tube. Typically environmentally summarizes the flow evaporator heating surface several Dampferzeu ¬ gerrohre, whereby it is advantageous if the exit ¬ diameter at the inlet header are smaller than the internal diameter of the steam generator tubes.
Grundsätzlich wäre auch eine Kombination von Drosseln, Nippeln mit kleinerem Innendurchmesser und/oder ein im Vergleich zum Innendurchmesser der Dampferzeugerrohre kleinerem Austrittsdurchmesser am Eintrittssammler als Maßnahmen zur lokalen Querschnittsverengung in jeweils anderen Dampferzeuger- rohren denkbar. Basically, a combination of throttles, nipples with a smaller inner diameter and / or a smaller compared to the inner diameter of the steam generator tubes outlet diameter at the inlet collector as measures for local cross-sectional constriction in each other steam generator tubes conceivable.
Die solarthermische Durchlaufverdampfer-Heizfläche ist dabei nach besonders vorteilhafter Ausgestaltung in ein Solarturm- Kraftwerk integriert und zur Dampferzeugung durch fokussierte Sonnenstrahlung direkt beaufschlagbar. The solar thermal continuous evaporator heating surface is integrated according to a particularly advantageous embodiment in a solar tower power plant and directly for steam generation by focused solar radiation acted upon.
Nachfolgend werden anhand von Zeichnungen Ausführungsbeispie¬ le der Erfindung beschrieben. Darin zeigen: Below are described with reference to drawings Ausführungsbeispie ¬ le of the invention. Show:
FIG 1 ein Heliostatenfeld und einen Solarturm eines So¬ larturm-Kraftwerks , 1 shows a heliostat field and a solar tower of a Sun ¬ larturm power plant,
FIG 2 einen Verdampfer eines solarthermischen Dampferzeugers nach dem Stand der Technik, 2 shows an evaporator of a solar thermal steam generator according to the prior art,
FIG 3 einen Zwangdurchlaufdampferzeuger mit einer solarthermischen Durchlaufverdampfer-Heizfläche, 3 shows a forced-circulation steam generator with a solar thermal continuous evaporator heating surface,
FIG 4 ein Dampferzeugerrohr mit Drossel, 4 shows a steam generator tube with throttle,
FIG 5 einen Eintrittssammler mit Dampferzeugerrohren, die über Nippel mit dem Eintrittssammler verbunden sind und FIG 6 einen Eintrittssammler mit Dampferzeugerrohren, wobei Austrittsdurchmesser am Eintrittssammler kleiner sind, als Innendurchmesser der Dampferzeugerrohre . Einander entsprechende Teile sind in den Figuren mit den gleichen Bezugszeichen versehen. 5 shows an inlet collector with steam generator tubes, which are connected via nipples to the inlet header and 6 shows an inlet header with steam generator tubes, wherein outlet diameters at the inlet header are smaller than the inside diameter of the steam generator tubes. Corresponding parts are provided in the figures with the same reference numerals.
FIG 1 zeigt den solaren Teil eines Solarturm-Kraftwerks 1. Das Solarturm-Kraftwerk 1 umfasst einen Solarturm 2, an des- sen vertikal oberem Ende ein Absorber 3 angeordnet ist. Ein Heliostatenfeld 4 mit einer Anzahl von Heliostaten 5 ist am Boden um den Solarturm 2 herum platziert. Das Heliostatenfeld 4 mit den Heliostaten 5 ist für eine Fokussierung der direkten Solarstrahlung 6 ausgelegt. Dabei sind die einzelnen He- liostaten 5 so angeordnet und ausgerichtet, dass die direkte Solarstrahlung 6 von der Sonne in Form von konzentrierter Solarstrahlung 7 auf den Absorber 3 fokussiert wird. Bei dem Solarturm-Kraftwerk 1 wird somit die Sonnenstrahlung durch ein Feld einzeln nachgeführter Spiegel, die Heliostaten 5, auf die Spitze des Solarturmes 2 konzentriert. Der Absorber 3 wandelt die Strahlung in Wärme um und gibt sie an ein Wärme¬ trägermedium, beispielsweise Wasser, ab, das die Wärme einem konventionellen Kraftwerksprozess mit einer Dampfturbine zu¬ führt . FIG. 1 shows the solar part of a solar tower power plant 1. The solar tower power plant 1 comprises a solar tower 2, at whose vertical upper end an absorber 3 is arranged. A heliostat field 4 with a number of heliostats 5 is placed on the ground around the solar tower 2. The heliostat 4 with the heliostat 5 is designed for focusing the direct solar radiation 6. In this case, the individual suspenders 5 are arranged and aligned such that the direct solar radiation 6 is focused by the sun in the form of concentrated solar radiation 7 onto the absorber 3. In the solar tower power plant 1, the solar radiation is thus concentrated on the tip of the solar tower 2 by a field of individually tracked mirrors, the heliostats 5. The absorber 3 converts the radiation into heat, and outputs it to a heat ¬ carrier medium, for example water, from which with a steam turbine, the heat leads to a conventional power plant process to ¬.
In FIG 2 ist eine Verdampferheizfläche 8 eines bekannten so¬ larthermischen Zwangumlaufdampferzeugers 9 mit Direktverdampfung dargestellt, der als Absorber 3 in den Solarturm 2 der FIG 1 integriert ist. In FIG 2 an evaporator 8 is of a known so ¬ larthermischen forced circulation steam generator 9 shown with direct evaporation, which is integrated as an absorber 3 in the solar tower 2 of Fig. 1
Die Dampferzeugerrohre 10 sind eingangsseitig mit einem Ein¬ trittssammler 11 und ausgangsseitig mit einem Austrittssammler 12 strömungstechnisch verbunden. Überströmrohre 13 verbinden den Austrittssammler 12 mit einer Trommel 14, in die eine Speisewasserleitung 15 mündet. In die Speisewasserlei¬ tung 15 ist eine Speisewasserpumpe 16 geschaltet. Eine Dampf¬ leitung 17 sowie eine Fallrohrleitung 18 zweigen von der Trommel 14 ab. In die Fallrohrleitung 18 ist eine Umwälzpumpe 19 geschaltet. Die Fallrohrleitung 18 mündet in den Eintrittssammler 11. The steam generator tubes 10 on the input side a ¬ occurs collector 11 and its output connected to a manifold 12 with an outlet fluidically. Overflow pipes 13 connect the outlet header 12 with a drum 14, into which a feedwater line 15 opens. In the Speisewasserlei ¬ device 15, a feedwater pump 16 is connected. A steam ¬ line 17 and a downcomer conduit 18 branch off from the drum fourteenth In the downpipe 18 is a circulation pump 19 switched. The downpipe 18 opens into the inlet header 11.
Im Betrieb des solar beheizten Zwangumlaufdampferzeugers 9 saugt die Umwälzpumpe 19 Kesselwasser aus der Trommel 14 an und drückt es in den Eintrittssammler 11. Dort wird das Kes¬ selwasser auf die Vielzahl der wärmeübertragenden Dampferzeugerrohre 10 verteilt. Die Verdampferheizfläche 8 ist in pa¬ rallel geschaltete Heizflächenrohre aufgeteilt. Die wärme- übertragenden Rohre 10 werden durch die konzentrierte Solarstrahlung 7 aufgeheizt, wobei die wärmeübertragenden Rohre 10 die Wärme an das Kesselwasser abgeben. Das entstehende In operation of the solar-heated forced-circulation steam generator 9, the pump sucks water from the boiler 19 to the drum 14 and presses it into the inlet header 11. There, the Kes ¬ selwasser is distributed to the plurality of heat-transferring steam generator tubes 10th The evaporator 8 is divided into parallel ¬ Heizflächenrohre. The heat-transferring tubes 10 are heated by the concentrated solar radiation 7, wherein the heat-transferring tubes 10 deliver the heat to the boiler water. The resulting
Dampf/Wasser-Gemisch wird über den Ausstrittssammler 12 und die Überströmrohre 13 in die unbeheizte Trommel 14 geleitet und dort in möglichst trockenen Sattdampf und in zur Verdampferheizfläche 8 zurückfließendes Umlaufwasser getrennt. Die Speisewasserzufuhr wird so geregelt, dass der Wasserstand in der Trommel 14 konstant bleibt. Der Sattdampf verlässt die Trommel 14 über die DampfleitungSteam / water mixture is passed through the outflow collector 12 and the overflow pipes 13 in the unheated drum 14 and separated there in saturated dry as possible and in circulating to the evaporator 8 backflow water. The feed water supply is controlled so that the water level in the drum 14 remains constant. The saturated steam leaves the drum 14 via the steam line
17 und kann in einer weiteren Heizfläche überhitzt werden und anschließend als Frischdampf einer nicht näher dargestellten Dampfturbine zur Erzeugung von elektrischer Energie zugestellt werden. 17 and can be overheated in a further heating surface and then delivered as live steam of a steam turbine not shown for generating electrical energy.
Zur Erläuterung des erfindungsgemäßen solarthermischen Durchlaufverdampfer-Heizfläche 20 im Solarturm-Kraftwerk 1 mit di¬ rekter Verdampfung zeigt FIG 3 das Prinzip eines solarthermischen Zwangdurchlaufdampferzeugers 21, bei dem der Durchlauf des Wasser-Dampf-Stromes durch die DurchlaufverdampferHeizfläche 20 von einer Speisewasserpumpe 16 erzwungen wird. Das Speisewasser wird von der Speisewasserpumpe 16 in den Eintrittssammler 11 und den Verdampfereintritt 22 gefördert und nacheinander werden die Dampferzeugerrohre 10 der Durch- laufverdampfer-Heizfläche 20 und der Überhitzer 23 durchströmt (bei solarthermischen Kraftwerken entfällt typischerweise ein Speisewasservorwärmer) . Die Erwärmung des Speisewassers bis zur Sattdampftemperatur, die Verdampfung und Überhitzung erfolgen kontinuierlich in einem Durchlauf, so dass keine Trommel benötigt wird. Zwischen Durchlaufverdamp- fer-Heizflache 20 und Überhitzer 23 ist für den Umlauf organg beim Anfahren der Anlage eine Abscheideeinrichtung 24 vorge- sehen. To explain the solar thermal DurchlaufverdampferHeizfläche 20 according to the invention in the solar tower power plant 1 with di ¬ rect evaporation FIG 3 shows the principle of a solar thermal once-through steam generator 21, in which the passage of the water-steam stream is forced by the DurchlaufverdampferHeizfläche 20 of a feedwater pump sixteenth The feed water is conveyed by the feed water pump 16 into the inlet header 11 and the evaporator inlet 22, and the steam generator tubes 10 of the continuous evaporator heating surface 20 and the superheater 23 are flowed through successively (in the case of solar thermal power plants, a feedwater pre-heater is typically omitted). The warming of the feed water to the saturated steam temperature, the evaporation and Overheating occurs continuously in one pass, so no drum is needed. Between the continuous evaporator heating surface 20 and the superheater 23, a separating device 24 is provided for circulation when the system starts up.
Mit Zwangdurchlaufdampferzeugern 21 können sehr große Dampfleistungen auf relativ kleinem Raum erzeugt werden. Durch de Wegfall der Abscheidetrommel können mit dem Durchlaufdampfer zeuger sehr hohe Drücke gefahren werden und somit auch sehr hohe Wirkungsgrade erzielt werden. With forced circulation steam generators 21 very large steam outputs can be generated in a relatively small space. By eliminating the separation drum generators very high pressures can be driven with the continuous steamer and thus very high efficiencies can be achieved.
FIG 4 zeigt eine bevorzugte Aus führungs form einer in ein Dampferzeugerrohr 10 der Durchlaufverdampfer-Heizfläche 20 des Durchlaufdampferzeugers 21 eingebauten lokalen Querschnittsverengung, die als Drossel 25 ausgeführt ist. FIG. 4 shows a preferred embodiment of a local cross-sectional constriction built into a steam generator tube 10 of the continuous evaporator heating surface 20 of the continuous-flow steam generator 21, designed as a throttle 25.
Hierzu ist in den Verdampfereintritt 22 jedes Dampferzeuger- rohrs 10 der Durchlaufverdampfer-Heizfläche 20 eine Drossel 25 geschaltet. For this purpose, a throttle 25 is connected in the evaporator inlet 22 of each steam generator tube 10 of the continuous evaporator heating surface 20.
Beim Betrieb des Durchlaufdampferzeugers 21 strömt konden¬ siertes Wasser, sogenanntes Speisewasser, aus einem der In operation of the continuous steam generator 21 from condensing ¬ overbased water, so-called feed water from a flow, the
(nicht gezeigten) Dampfturbine nachgeschalteten (nicht ge- zeigten) Kondensator über hier nicht dargestellte Vorwärmer und eine Speisewasserleitung 15 in den Eintrittssammler 11. Von dort strömt das vorgewärmte Speisewasser über die Dros¬ seln 25 in die einzelnen Dampferzeugerrohre 10 der solarthermischen Durchlaufverdampfer-Heizfläche 20. From there, the preheated feed water flows via the Dros ¬ nel 25 into the individual steam generator tubes 10 of the solar thermal continuous evaporator heating surface 20th ,
Die Drosseln 25 gewährleisten praktisch über den gesamten Lastbereich des solarthermischen Durchlaufdampferzeugers 21 einen erhöhten Druckverlust im Verdampfer. Dabei wird ein stabiler und gleichmäßiger Durchfluss des vorgewärmten Spei- sewassers durch die Dampferzeugerrohre 10 erzielt. The throttles 25 ensure virtually over the entire load range of the solar thermal continuous steam generator 21 an increased pressure drop in the evaporator. In this case, a stable and uniform flow of the preheated feed water through the steam generator tubes 10 is achieved.
FIG 5 zeigt eine alternative Querschnittsverengung, die da¬ durch erzielt wird, dass zwischen Eintrittssammler 11 und Dampferzeugerrohren 10 angeordnete Nippel 26 einen kleineren Innendurchmesser als die Dampferzeugerrohre 10 aufweisen. 5 shows an alternative cross-sectional constriction, which is as ¬ achieved by that between the inlet header 11 and Steam generator tubes 10 arranged nipple 26 have a smaller inner diameter than the steam generator tubes 10.
FIG 6 zeigt eine weitere Aus führungs form der lokalen Quer- schnittsverengung, die sich dadurch ergibt, dass Austrittsdurchmesser 27 am Eintrittssammler 11 kleiner sind, als Innendurchmesser 28 der Dampferzeugerrohre 10. 6 shows a further embodiment of the local cross-sectional constriction, which results from the fact that outlet diameters 27 at the inlet header 11 are smaller than the inside diameter 28 of the steam generator tubes 10.
Claims
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010040208.7 | 2010-09-03 | ||
| DE201010040208 DE102010040208B4 (en) | 2010-09-03 | 2010-09-03 | Solar thermal continuous evaporator heating surface with local cross-sectional constriction at its inlet |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| WO2012028494A2 true WO2012028494A2 (en) | 2012-03-08 |
| WO2012028494A3 WO2012028494A3 (en) | 2012-06-21 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/EP2011/064457 Ceased WO2012028494A2 (en) | 2010-09-03 | 2011-08-23 | Solar thermal continuous evaporator heating surface with local cross-sectional narrowing on the inlet thereof |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE102010040208B4 (en) |
| WO (1) | WO2012028494A2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012110346A1 (en) * | 2011-02-17 | 2012-08-23 | Siemens Aktiengesellschaft | Solar-thermal continuous evaporator having a local reduction in the cross-section on its inlet |
| CN103363159A (en) * | 2012-03-30 | 2013-10-23 | 巴尔克有限公司 | Throttle device |
| WO2012110329A3 (en) * | 2011-02-17 | 2014-04-10 | Siemens Aktiengesellschaft | Solar-thermal steam generator |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023174718A1 (en) * | 2022-03-15 | 2023-09-21 | Aalborg Csp A/S | Solar radiation receiver |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT278863B (en) * | 1968-01-15 | 1970-02-10 | Waagner Biro Ag | Process and device for equalizing the heat transfer |
| CH640631A5 (en) * | 1979-06-20 | 1984-01-13 | Bbc Brown Boveri & Cie | HEAT EXCHANGER. |
| US4577593A (en) * | 1984-11-08 | 1986-03-25 | Combustion Engineering, Inc. | Waterwall tube orifice mounting assembly |
| WO1997014930A2 (en) * | 1995-10-17 | 1997-04-24 | Siemens Aktiengesellschaft | Method and device for producing solar steam |
| KR100439080B1 (en) * | 1997-06-30 | 2004-07-05 | 지멘스 악티엔게젤샤프트 | Waste heat steam generator |
| DE19858780C2 (en) * | 1998-12-18 | 2001-07-05 | Siemens Ag | Fossil-heated continuous steam generator |
| DE19914761C1 (en) * | 1999-03-31 | 2000-09-28 | Siemens Ag | Fossil fuel through-flow steam generator for electrical power plant has vertical evaporator pipes defined by walls of combustion chamber formed in loop at interface between combustion chamber and horizontal gas flue |
| US20090260622A1 (en) * | 2008-04-16 | 2009-10-22 | Alstom Technology Ltd | Solar steam generator having a standby heat supply system |
-
2010
- 2010-09-03 DE DE201010040208 patent/DE102010040208B4/en not_active Revoked
-
2011
- 2011-08-23 WO PCT/EP2011/064457 patent/WO2012028494A2/en not_active Ceased
Non-Patent Citations (1)
| Title |
|---|
| None |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012110346A1 (en) * | 2011-02-17 | 2012-08-23 | Siemens Aktiengesellschaft | Solar-thermal continuous evaporator having a local reduction in the cross-section on its inlet |
| WO2012110329A3 (en) * | 2011-02-17 | 2014-04-10 | Siemens Aktiengesellschaft | Solar-thermal steam generator |
| CN103363159A (en) * | 2012-03-30 | 2013-10-23 | 巴尔克有限公司 | Throttle device |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2012028494A3 (en) | 2012-06-21 |
| DE102010040208B4 (en) | 2012-08-16 |
| DE102010040208A1 (en) | 2012-03-08 |
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