WO2012028517A2 - Évaporateur continu solaire thermique - Google Patents

Évaporateur continu solaire thermique Download PDF

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Publication number
WO2012028517A2
WO2012028517A2 PCT/EP2011/064564 EP2011064564W WO2012028517A2 WO 2012028517 A2 WO2012028517 A2 WO 2012028517A2 EP 2011064564 W EP2011064564 W EP 2011064564W WO 2012028517 A2 WO2012028517 A2 WO 2012028517A2
Authority
WO
WIPO (PCT)
Prior art keywords
evaporator
collector
tubes
solar
tube section
Prior art date
Application number
PCT/EP2011/064564
Other languages
German (de)
English (en)
Other versions
WO2012028517A3 (fr
Inventor
Joachim Brodesser
Martin Effert
Joachim Franke
Original Assignee
Siemens Aktiengesellschaft
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 Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO2012028517A2 publication Critical patent/WO2012028517A2/fr
Publication of WO2012028517A3 publication Critical patent/WO2012028517A3/fr

Links

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
    • 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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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
    • F22B21/02—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from substantially straight water tubes
    • F22B21/20—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from substantially straight water tubes involving sectional or subdivided headers in separate arrangement for each water-tube set
    • 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
    • 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
    • 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
    • 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 continuous evaporator with evaporator tubes, which are connected with their inlet ends to an inlet header and with their outlet ends to an outlet header.
  • Solar thermal power plants are therefore an alternative to conventional electricity generation. Solar thermal power plants are currently being implemented 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 solar tower and direct evaporation consists of a solar field, the solar tower and a conventional power plant part in which the thermal energy of the water vapor is converted into electrical energy ⁇ .
  • the solar field consists of heliostats that focus their light on ei ⁇ nen housed in the tower absorbers.
  • the absorber consists of a heating area in which the inserted ⁇ radiated solar energy is used to heat supplied to feed water to evaporate and possibly also to overheat.
  • the generated steam is then expanded in a conventional power plant ball in a turbine, and then condensed to the absorber again to ⁇ .
  • the turbine drives a generator, which converts the me ⁇ chanic energy into electrical energy.
  • the heating of a number of evaporator tubes, which together form an evaporator heating surface leads to a complete evaporation of a flow medium in the evaporator tubes in one pass. Before it evaporates, the flow medium-usually water-can be fed to a preheater upstream of the evaporator heating surface, also referred to as an economizer, and preheated there.
  • the evaporator tubes In solar-heated through steam generators the evaporator tubes have at the outlet of the evaporator often large ⁇ SSE temperature differences, since different amounts of heat is transferred to the individual vapor ⁇ ferrohre the parallel pipe system. The causes of different amounts of heat transferred are due to the locally very different heat flux densities of the incident on the absorber bundled sunlight.
  • the solar energy input 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 results in very high heat flux densities, generally higher heat flux densities, than in fossil-fired thermal power plants by concentrating the irradiated solar energy on small areas. 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, the highest possible heat flow densities are to be increased.
  • the upper limit of the permissible heat flow densities is determined by the pipe material and the quality of the cooling mechanisms.
  • continuous steam generators are not subject to any pressure limitation, so that live steam pressures well above the critical pressure of water are possible. This high live steam pressure promotes a high thermodynamic efficiency of a power plant.
  • the pressure loss of the steam line acts like a throttle at the outlet of the system and is destabilizing.
  • the proportion of this pressure loss at the Ge ⁇ feldruckpar of the system is to minimize the occurrence of a stability Insta.
  • flow oscillations in evaporators only occur in systems having at least two flow forms, where one phase must be incompressible medium, i. in this case supercooled water.
  • An object of the invention is, therefore, the evaporator tubes of a solar-heated through steam generator so summarizegestal ⁇ th that despite the different heat-absorption of individual evaporator tubes and in spite of high heat flux densities, destabilized ⁇ sierende pressure losses are minimized and thereby a formed for the overall system instability is prevented. This should be achieved at low cost.
  • this object is achieved for solar-heated through ⁇ running steam generator of the type mentioned by a combination of the features of claim 1.
  • the solar-heated continuous steam generator to an evaporator comprising a manifold, a collector and evaporator tubes, wherein the manifold is connected to the collector via a number of evaporator tubes, andarguess ⁇ least one through-collector is connected in the evaporator tubes.
  • a first evaporator pipe section between the distributor and the passage collector which defines a first evaporator part surface and a second evaporator ⁇ ferrohrab mustard formed between the passage collector and the collector, which defines a second evaporator part surface.
  • the passage collector is thus switched between the first evaporator tube section and the second evaporator tube section .
  • a pressure equalization between the evaporator tubes of the first evaporator subarea and the second evaporator subarea is made possible by the passage collector.
  • the throughput collector is a pressure vessel with a number of connections for evaporator tubes.
  • each evaporator tube from the first evaporator tube section opens at a height H, starting from the distributor, into a passage collector, from which in turn the tubes of the second evaporator tube section are discharged. Due to the pressure equalization, the two evaporator pipe sections are decoupled on the flow side.
  • the relatively high due to the relatively large ⁇ SEN flow velocity Reibungstikver ⁇ loss in the second evaporator section therefore has no training effects on the flow conditions in the first evaporator section.
  • temperature imbalances (tempera ⁇ turfall over the evaporator tube wall) due to Mehrbe ⁇ heaters individual tubes at the outlet of the first evaporator tube section are minimized.
  • the maximum height H of the passage collector is thereby be ⁇ true that dynamic instabilities of the fluid in the ⁇ ers th evaporator tube section is reliably avoided.
  • dynamic Instabili ⁇ activities only occur if there is still undercooled medium at the entrance to this heating. This is avoided by a suitably selected size of the heating surface sections.
  • the minimum height H is determined by minimizing water and vapor phase segregations in the throughput collector. For this, at least a mean vapor content in the throughput collector at the lowest load in continuous operation of 60% is required.
  • the choice of a collector passage has opposite a simp ⁇ chen pressure equalization between the evaporator tubes has the advantage that the number of parallel tubes in the first and second evaporator tube section may be different.
  • the evaporator tubes of the first evaporator tube section Kgs ⁇ NEN be connected to the evaporator tubes of the second evaporator tube section via a frictional connection with each other.
  • FIG 3 shows an evaporator tube with connection to a passage collector.
  • the solar tower power plant 1 comprises a solar tower 2, at the vertical upper end of an absorber 3, for example in the form of a Verdampferwandsammlung phenomenon 8 (see FIG 2) is arranged.
  • a He ⁇ liostatenfeld 5 with a number of heliostats 6 is on the soil placed around the solar tower 2 around.
  • the heliostat 5 with the heliostat 6 is designed for focusing the direct solar radiation I s .
  • the individual helix states 6 are arranged and aligned such that the direct solar radiation I s is focused by the sun in the form of concentrated solar radiation I c onto the absorber 3.
  • the solar radiation is thus concentrated by a field individually tracked mirror, the heliostat 6, on the top of the solar tower 2.
  • an absorber 3 for example an Ver ⁇ dampferwandsammlung reaction 8 in heat Umwan ⁇ delt and to a heat transfer medium, for example water, which emits radiation I c, which supplies the heat to a conventional power station process with a steam turbine.
  • a solar thermal continuous evaporator 7 is shown, as it is integrated in an advantageous embodiment as Verdampferwandsammlung procedure 8 in the absorber 3 of the solar tower power plant 1 of FIG 1.
  • Concentrated solar radiation I c hits focused on a plurality of heat-transmitting tubes, the so-called evaporator tubes 9.
  • the evaporator tubes 9 are fluidly connected on the input side at the evaporator inlet with a manifold 11. At the evaporator outlet, the evaporator tubes 9 are connected to a collector 13.
  • the evaporator tubes are heated by the concentrated solar radiation ⁇ I c 9, wherein the evaporator tubes 9, the Wär ⁇ me of a flow medium, such as water, exits.
  • the flow medium is vaporized directly in the evaporator tubes 9 by the concentrated solar radiation I c .
  • the vaporized water leaves the evaporator outlet and may, if appropriate, further overheating in a heating surface, not shown, in a non-illustrated conventional power plant part for relaxation in a
  • the vapor available at the evaporator outlet can, if appropriate overheating, optionally be delivered in a further heating area (not shown) as live steam to the steam turbine (not shown) for generating electrical energy.
  • FIG. 3 essentially shows a vertical section through an evaporator tube 9, a distributor 11, a collector 13 and a passage collector 14.
  • the evaporator tube 9 consisting of a first evaporator tube section 20 and a second evaporator tube section 21.
  • the first evaporator tube section 20 terminates at the height H and is connected there to a passage collector inlet tube 15.
  • the passage collector inlet pipe 15 is in turn connected to the passage collector 14.
  • a plurality of evaporator tubes 9 is present. Due to the ThomasZeichnung these are not shown in FIG.
  • Each of the evaporator tubes is connected to the passage collector 14 via a passage collector inlet pipe 15, so that a plurality of through-collector inlet pipes 15 is connected to the passage collector 14.
  • the passage collector inlet tube 15 may be part of the evaporator tube 9.
  • the height H is the distance between the distributor 11 and the connection of the evaporator tube 9 to the passage collector 14.
  • a structure formed in the first evaporator tube section 20 is thus formed.
  • Steam or water / steam mixture via the passage collector inlet pipe 15 in the passage collector 14 can be conducted.
  • a different pressure ratio between the individual evaporator tubes 9 in the first evaporator tube section 20 is thus compensated by the passage collector 14.
  • a throughflow outlet pipe 16 is connected to the throughflow collector 14, which connects the throughflow collector 14 to the evaporator pipe 9 of the second evaporator pipe section 21.
  • the collected steam is thus divided again via a multiplicity of throughflow collector outlet pipes 16 to the individual evaporator pipes 9 of the second evaporator pipe section 21.
  • the through ⁇ profile collector outlet tubes 16 of the evaporator tubes ⁇ 9 may be.
  • the number of through-collector inlet pipes (15) and the number of through-collector outlet pipes (16) may be different.
  • the evaporator tubes 9 can not be configured continuously. In order to nevertheless ensure 9 required stability for the mechanical stress of the evaporator tubes a frictional connection 17 is provided at each ⁇ the evaporator tube which 9 connects the evaporator tubes of the first evaporator ⁇ pipe section 20 with the evaporator tubes 9 of the second evaporator tube section 21st

Abstract

L'invention concerne un évaporateur continu (1) solaire thermique comprenant un répartiteur (11) et un collecteur (13), ledit répartiteur (11) étant relié au collecteur (13) par l'intermédiaire d'un certain nombre de tubes évaporateurs (9). Selon l'invention, un collecteur de passage est raccordé dans les tubes évaporateurs (9) de sorte à former un premier segment de tubes évaporateurs (20) entre le répartiteur (11) et le collecteur de passage (14) ainsi qu'un second segment de tubes évaporateurs (21) entre le collecteur de passage (14) et le collecteur (13).
PCT/EP2011/064564 2010-09-03 2011-08-24 Évaporateur continu solaire thermique WO2012028517A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010040204A DE102010040204A1 (de) 2010-09-03 2010-09-03 Solarthermischer Durchlaufverdampfer
DE102010040204.4 2010-09-03

Publications (2)

Publication Number Publication Date
WO2012028517A2 true WO2012028517A2 (fr) 2012-03-08
WO2012028517A3 WO2012028517A3 (fr) 2012-06-21

Family

ID=44677851

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/064564 WO2012028517A2 (fr) 2010-09-03 2011-08-24 Évaporateur continu solaire thermique

Country Status (2)

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DE (1) DE102010040204A1 (fr)
WO (1) WO2012028517A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103062743B (zh) * 2013-01-09 2015-07-29 北京世纪源博科技股份有限公司 一种腔体式自然循环式太阳能饱和蒸汽锅炉
CN109282266A (zh) * 2018-07-30 2019-01-29 缙云县田农新能源科技有限公司 一种生物燃烧锅炉集汽器及安装使用方法

Family Cites Families (6)

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Publication number Priority date Publication date Assignee Title
DE444588C (de) * 1926-02-28 1927-05-23 Heinrich Lanz Akt Ges Dampfueberhitzer
US3358650A (en) * 1965-12-27 1967-12-19 Combustion Eng Water cooled furnace joint for mixing header arrangement
DE4142376A1 (de) * 1991-12-20 1993-06-24 Siemens Ag Fossil befeuerter durchlaufdampferzeuger
EP1794495B1 (fr) * 2004-09-23 2017-04-26 Siemens Aktiengesellschaft Generateur de vapeur en continu chauffe a l'aide d'un combustible fossile
KR101268364B1 (ko) * 2008-03-27 2013-05-28 알스톰 테크놀러지 리미티드 이퀄라이징 챔버를 가진 연속 스팀 발생기
US20090260622A1 (en) * 2008-04-16 2009-10-22 Alstom Technology Ltd Solar steam generator having a standby heat supply system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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Publication number Publication date
WO2012028517A3 (fr) 2012-06-21
DE102010040204A1 (de) 2012-03-08

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