US20160040909A1 - Absorber arrangement for a trough collector - Google Patents

Absorber arrangement for a trough collector Download PDF

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Publication number
US20160040909A1
US20160040909A1 US14/409,400 US201314409400A US2016040909A1 US 20160040909 A1 US20160040909 A1 US 20160040909A1 US 201314409400 A US201314409400 A US 201314409400A US 2016040909 A1 US2016040909 A1 US 2016040909A1
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United States
Prior art keywords
absorber
arrangement
heat
fluid
length
Prior art date
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Abandoned
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US14/409,400
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English (en)
Inventor
Andrea Pedretti-Rodi
Gianluca Ambrosetti
Sergio Granzella
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Airlight Energy IP SA
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Airlight Energy IP SA
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Publication date
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Assigned to AIRLIGHT ENERGY IP SA reassignment AIRLIGHT ENERGY IP SA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMBROSETTI, Gianluca, GRANZELLA, Sergio, PEDRETTI-RODI, Andrea
Publication of US20160040909A1 publication Critical patent/US20160040909A1/en
Abandoned legal-status Critical Current

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Classifications

    • F24J2/12—
    • 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
    • F24J2/26—
    • 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
    • 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
    • F24S10/75—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits with enlarged surfaces, e.g. with protrusions or corrugations
    • 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
    • F24S23/74—Arrangements for concentrating solar-rays for solar heat collectors with reflectors with trough-shaped or cylindro-parabolic reflective surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S30/00—Arrangements for moving or orienting solar heat collector modules
    • F24S30/40—Arrangements for moving or orienting solar heat collector modules for rotary movement
    • F24S30/42—Arrangements for moving or orienting solar heat collector modules for rotary movement with only one rotation axis
    • F24S30/425—Horizontal axis
    • 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
    • F24S2023/88—Multi reflective traps
    • 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
    • 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
    • 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
    • Y02E10/47—Mountings or tracking

Definitions

  • the present invention relates to an absorber arrangement for a trough collector plant according to the preamble of claim 1 .
  • Trough collectors of the stated type are used among other things in solar power plants.
  • the radiation of the sun is reflected by the concentrator of collectors and focused in a targeted manner on a location in which high temperatures arise as a result.
  • the concentrated heat can be conducted away and used to operate thermal engines such as turbines which in turn drive the generators which generate electricity.
  • the dish/Sterling systems as small units in the range of up to 50 kW per module have generally not caught on.
  • Solar tower plant systems have a central absorber which is mounted in an elevated manner (on the “tower”) for the sunlight which is reflected to it by means of hundreds to thousands of individual mirrors, whereby the radiation energy of the sun is concentrated in a punctiform manner in the absorber by means of the many mirrors or concentrators and on account of the thus achievable high concentration, temperatures of up to 1300° C. can be reached, which is favourable for the efficiency of the downstream thermal engines (generally a steam or fluid turbine power plant for electricity generation).
  • Solar tower power plants have hitherto likewise not become widespread (in spite of the advantageously achievable high temperatures), due to the somewhat difficult technology which is intrinsic to them.
  • Parabolic trough systems are widespread however and have a large number of trough collectors which have long concentrators having small transverse dimensions and therefore do not have a focal point but a focal line, which fundamentally distinguishes these in their design from the dish Stirling and solar tower power plants.
  • These linear concentrators today have a length of 20 m to 150 m whilst the width can reach 5 m or 10 m and more.
  • An absorber line for the concentrated heat (up to nearly 500° C.) is arranged in the focal line, wherein a medium, which absorbs the heat and transports the same via lines to the machine hall of the power plant, flows through the absorber line.
  • a fluid such as e.g. thermal oil or superheated steam are possibilities for the heat-transporting medium.
  • the power plant “Nevada Solar One”, connected to the mains in 2007, has trough collectors with 182,400 curved mirrors, which are arranged on an area of 140 hectares, and produces 65 MW.
  • the plants Andasol 1 to 3 should have a maximum outlet of 50 MW (Andasol 3 entered into operation at the end of 2011). For the plant as a whole (Andasol 1 to 3), a peak efficiency of approx. 20% and also an annual average efficiency of about 15%.
  • the emission or radiation of heat via the lines in which the heat-transporting medium circulates (heat loss).
  • This may reach 100 W/m, with a line length of the order of magnitude of up to 100 km, so that the heat losses over the lines are of considerable importance for the overall efficiency of the power plant, also including the absorber pipes' proportion of heat losses. From the above information, it follows that the entire length of the trough collectors and accordingly also that of the absorber pipes in such solar plants reaches dozens of kilometres, thus the heat losses thereof cannot be neglected for the efficiency of the plant as a whole.
  • the absorber lines are built increasingly complexly in order to avoid such energy losses.
  • widespread conventional absorber lines are constructed as a metal pipe enveloped by glass, wherein a vacuum prevails between the glass and metal pipe.
  • the metal pipe conveys the heat-transporting medium in its interior and is provided on its outer surface with a coating which better absorbs the incident light in the visible range, but has a deep emission rate for wavelengths in the infra-red range.
  • the enveloped glass pipe protects the metal pipe from cooling by means of the wind and acts as an additional barrier for heat radiation. It is disadvantageous that the enveloping glass wall partly likewise reflects or even absorbs incident concentrated solar radiation, which means that a layer reducing the reflection is applied to the glass.
  • the absorber line can additionally be provided with a mechanical protection pipe which envelops it and which although it must be supplied with an opening for the incident solar radiation, otherwise protects the absorber line very reliably.
  • WO 2010/078 668 (which is here included in the present application by way of reference) an externally-insulated absorber pipe with improved efficiency is disclosed, the elongated thermal opening of which exists on account of the use in a trough collector and is constructed as a slot opening and is optimised with regards to the heat losses, in that the thermal opening is made smaller over the length of the absorber pipe in accordance with the longitudinally-increasing temperature of the heat-transporting medium which flows longitudinally through the absorber pipe.
  • the complex measures for making the thermal opening smaller are only performed in a comparatively small area of the absorber pipe.
  • a heat exchanger arrangement which is constructed for the throughflow of the heat-transporting fluid in transverse flow, is provided means that the absorber space can be constructed in such a manner by means of the separation of the at least one absorber space from the heat exchanger, through which fluid flows, that even at high temperatures of more than 500° C., for example up to 650° C. or even higher, the heat radiation through the thermal opening thereof falls to a lesser extent and as a result, the efficiency of the heat-exchanger arrangement as a whole is improved.
  • FIG. 1 shows a trough collector with an absorber pipe of conventional type
  • FIG. 2 shows a view onto a section of a first embodiment of the absorber arrangement according to the invention
  • FIG. 3 shows a view onto a section of a second embodiment of the absorber arrangement according to the invention
  • FIG. 4 shows a view onto a section of a third embodiment of the absorber arrangement according to the invention
  • FIG. 5 shows a view onto an absorber space formed by a part of the heat-exchanger arrangement
  • FIG. 6 shows a cross section through a trough collector with an absorber arrangement according to the invention, which has at least two parallel mutually adjacently arranged longitudinally running absorber spaces, and
  • FIG. 7 shows a cross section through the absorber arrangement of FIG. 6 .
  • FIG. 1 shows a trough collector 1 of conventional type, with a concentrator 2 which is parabolically curved in cross section and reflects incident solar rays 3 , wherein the reflected rays 4 are concentrated into a focal line region in which an absorber pipe 5 is arranged.
  • the absorber pipe 5 Via a supply line 6 , the absorber pipe 5 is fed with a heat-transporting medium which flows through the same, is heated in the process from an inlet temperature T E to an outlet temperature T A and finally is conducted away by means of a drain 7 .
  • Schematically illustrated links 8 allow the pivoting of the concentrator 2 about the pivot axis 10 , so that the concentrator 2 can constantly be made to track the current position of the sun.
  • Bearings 11 for the concentrator 2 and the lines 6 , 7 are likewise schematically illustrated.
  • the profile of the temperature T of the heat-transporting medium over the length L of the absorber pipe 5 is qualitatively illustrated by means of the curve 15 .
  • the temperature curve 15 is essentially linear, in accordance with the heat supplied evenly over the length L to the absorber pipe (and thus the fluid flowing longitudinally through the same) by means of the reflected rays 4 .
  • the absorber pipe 5 has a thermal opening, which is not illustrated so as not to overload the figure, through which the rays pass into the interior of the absorber pipe 5 and heat the heat-transporting fluid.
  • An arrangement of this type is known to the person skilled in the art from the above-mentioned WO 2010/078 668.
  • the interior of the absorber pipe 5 (including the heated heat-transporting fluid) heated by the reflected rays 4 radiates heat in the infra-red range, wherein this heat back radiation or reemission escapes from the absorber pipe through the thermal opening. This back radiation or reemission increases with the fourth power of the temperature prevailing in the interior of the absorber pipe 5 .
  • the curve 16 qualitatively shows the profile of the radiation intensity through the thermal opening of the absorber pipe 5 .
  • the absorber pipe continuously loses energy with the fourth power of the internal temperature thereof, so that a fundamentally desirable further increase of the outlet temperature T A from 500° C. to for example 650° C. or more is problematic, because, among other reasons, the back radiation or remission is just as high after a certain length of the absorber pipe 5 as the irradiation by means of the reflected rays 4 , so that a further increase of the temperature in the fluid no longer takes place.
  • FIG. 2 schematically shows an absorber arrangement 20 according to the present invention, as can be used in the place of the absorber pipe 5 in a trough collector ( FIG. 1 ). Only a longitudinal section 21 of the absorber arrangement 20 is illustrated in the figure, starting with a cross section through the absorber arrangement 20 at any desired point along the length thereof and a view of the longitudinal section 21 through to a section line 22 following the cross section, wherein the absorber arrangement 20 continues after the section line 22 through to the end of the respective trough collector.
  • absorber arrangements in a length greater than 100 m, preferably greater than 150 m and preferably up to 200 m or more may be realised according to the invention, which allows correspondingly long trough collectors and is beneficial for the industrial deployment of trough collectors in a solar power plant.
  • a supply arrangement here constructed as pipelines 23 , 24
  • a drain arrangement here constructed as pipelines 25
  • the pipelines 26 lie next to one another in two rows 27 and 28 and form a heat-exchanger arrangement 29 .
  • the row 28 is indicated by means of the contours of the mutually adjacent pipelines 26 , the row 27 is covered in the view illustrated.
  • Walls 36 of the absorber space 30 absorb the heat of the heat incident by means of the rays 4 and pass this on to the pipelines 26 of the heat-exchanger arrangement 29 , to which they are thermally connected, for example by means of direct contact with the walls 36 , as is illustrated in the figure.
  • heat-transporting fluid is supplied to the pipelines 26 of the heat-exchanger arrangement 29 over the length L with the inlet temperature T E by means of the inlet sections 38 of the pipelines 23 , 24 of the supply arrangement, wherein the fluid is heated to the outlet temperature T A in the pipelines 26 and is passed at this temperature from the outlet sections 39 to the pipeline 25 of the drain arrangement, likewise over the length L of the absorber arrangement.
  • the heat-transporting fluid flows longitudinally through the absorber arrangement as before, but it two separate flows, once with the inlet temperature T E and once with the outlet temperature T A , as is symbolised by the flow arrows in the figure. Furthermore, it follows that the heat-transporting fluid is moved in a direction crosswise to the length of the absorber arrangement during the absorption of heat.
  • the absorber space 30 can be laid out once in terms of its shape by the person skilled in the art in such a manner that for a given concentrator 2 ( FIG. 1 ), principally the inlet region of the absorber space 30 is illuminated by the rays 4 .
  • the fluid In the inlet region close to the thermal opening 35 , the fluid has another low temperature close to the inlet temperature T E , with the consequence that the inlet region is strongly cooled, thus the heat reflection/reemission thereof is correspondingly low.
  • the thermal opening 35 overwhelmingly “sees” the inlet region, much less however the (far away, rearmost) wall of the absorber space 30 which is opposite the inlet region and for its part is heated to the outlet temperature T A .
  • the absorber spaces illustrated in the figures are constructed beneficially in this respect.
  • the person skilled in the art can achieve the enlargement of the heat-exchanging surface.
  • the entire inner surface of the pipelines 26 of the heat-exchanger arrangement is used as heat-exchanging surface.
  • the pipelines 26 are heated virtually evenly all the way round by the conduction of heat in the material of the pipelines 26 (for example a good heat-conducting material such as copper or a suitable alloy, conducting heat well at higher temperatures), so that the heat-exchanging surface is correspondingly large.
  • a large heat-exchanging surface is used for the efficient heat transfer to the heat-transporting fluid, so that a local overheating of the heat-exchanging surface can be substantially prevented.
  • the relevant wall regions of the absorber pipe located close to the thermal opening remain cooler and an overheating of the heat-exchanging surfaces is substantially reduced than in the case of a conventional absorber pipe.
  • thermal opening depending on the design of the absorber pipe, is designated as a physical opening for the absorber space according to FIG. 2 .
  • the term “thermal opening” also comprises a physically closed region in the case of other designs of the absorber space, which region is designed for the passage of heat of the concentrated solar radiation, wherein for example, by means of suitable coatings at the location of the heat irradiation, a reflection of the heat can be minimised. Designs of this type are known to the person skilled in the art. Nonetheless, it is necessarily the case, that at the location of the thermal opening, ultimately it is not possible to achieve good insulation, thus the corresponding relevant heat losses due to heat reflection/reemission must be accepted.
  • the absorber arrangement according to the invention can be used in a trough collector only a short distance from the edge thereof, for example after the fluid has reached a temperature of 100° C. or somewhat more.
  • An absorber arrangement according to the present invention extending over the entire length of the trough collector is preferred however.
  • the pipelines 26 of the heat-exchanger arrangement 29 can replace the walls of the absorber space 30 at least to some extent, with the advantage that as a result, the pipelines 26 are directly irradiated, that is to say the heat transfer to the heat-transporting fluid is only impeded minimally. It is likewise compliant with the invention if at least sections of the wall of the at least one absorber space are formed by the heat exchanger or the pipelines thereof. Further, it is compliant with the invention that the heat exchanger has mutually adjacent line sections for the fluid, which form at least one wall section for the at least one absorber space.
  • the absorber space may for example be formed by lines 42 of the heat-exchanger arrangement, as the same run in mutually adjacent windings and thus preferably completely envelop the interior of the absorber space.
  • FIG. 3 shows a further embodiment of the absorber arrangement 40 according to the present invention, which essentially corresponds to that of FIG. 2 , except for the construction of the heat-exchanger arrangement 41 , whose lines, which are constructed as pipelines 42 , are here laid in small loops, that is to say are constructed longer in each case.
  • the heat-exchanging fluid flows through the heat-exchanger arrangement 41 in transverse flow with respect to the longitudinal direction L.
  • the tube 24 ( FIG. 2 ) is omitted in the FIG. 3 , in order to make it possible to see the pipelines 42 .
  • the small flow arrows 44 show the direction of flow of the heat transporting fluid.
  • FIG. 4 shows yet a further embodiment of an absorber arrangement 50 according to the present invention, which essentially corresponds to that of FIG. 2 , except in turn for the construction of the heat-exchanger arrangement 51 , whose lines, which are constructed as pipelines 52 , are here laid in small coils 53 , that is to say are constructed even longer in each case.
  • the coils 53 are only indicated schematically in the Figure and illustrated in detail in FIG. 5 .
  • the coils 53 formed from the pipelines 52 are open towards the bottom and as a result form absorber spaces 54 , as a space section is enclosed by them. As a result, the heat-exchanging surface for this room section and thus also over the length of the absorber arrangement 50 gets substantially larger, with the advantages as mentioned above for FIG. 1 .
  • the regions of the coils 53 open at the bottom form thermal openings 59 .
  • the absorber spaces 54 lie in a row 55 due to the shown arrangement of the coils 53 .
  • FIG. 4 also, the pipeline 24 has been omitted so as not to overload the figure, so that the view onto the coils 53 becomes clear.
  • the absorber arrangement 50 in the embodiment illustrated in the figure is constructed in such a manner that the supply arrangement and the drain arrangement have a supply pipe 23 , 24 and a drain pipe 25 , wherein the pipes 23 , 24 , 25 run parallel to one another and the here numerous absorber spaces each formed by a coil 53 are arranged between these pipes 23 to 25 and extend over the length of the absorber arrangement 50 .
  • FIG. 5 shows a view of one of the coils 53 only indicated schematically in FIG. 4 , formed from the windings of a line of the heat-exchanger arrangement 51 according to the invention, here constructed as a pipeline 52 .
  • the coil 53 here has an axis of symmetry 55 and encloses an absorber space 54 for the incident radiation 4 , wherein the end of the coil 53 which is open at the bottom forms a thermal opening 59 .
  • Heat-transporting medium at the inlet temperature T E flows through the connecting piece 57 of the pipeline 52 into the coil 53 , flows through the same and is passed through the end section 58 of the pipeline 52 at the outlet temperature T A into a collecting line, here constructed as pipeline 25 .
  • an absorber arrangement results, in which the supply arrangement and the drain arrangement have a supply pipe 23 , 24 and a drain pipe 25 , wherein the pipes 23 , 24 , 25 run parallel to one another and a number of absorber spaces 54 is provided, which are arranged in at least one row 55 running between these pipes 23 , 24 , 25 , wherein the at least one row 55 extends over the length of the pipes.
  • a plurality of absorber spaces are provided, which are connected parallel between the supply and the drain arrangements.
  • FIG. 6 shows a cross section through a trough collector 60 , with an absorber arrangement 61 according to the invention, wherein two concentrators 62 and 63 are provided, which are for example configured according to WO 2010/037 243 (which is here included by reference in the present application).
  • the framework of the trough collector 60 is for example constructed in accordance with WO 2009/135 330.
  • the absorber arrangement 61 has at least two absorber spaces 64 and 65 which extend over the length L of the absorber arrangement 61 .
  • it is also compliant with the invention to provide two rows of absorber spaces arranged one behind the other, analogously to the embodiments according to FIGS. 3 to 5 , in which absorber spaces arranged in rows are illustrated.
  • it may be added that it is likewise compliant with the invention to provide more than two rows of absorber spaces in an absorber arrangement in the case of trough collectors with even more mutually adjacent concentrators.
  • FIG. 7 shows a cross section through the absorber arrangement 61 of FIG. 6 . Illustrated is a line of a supply arrangement for heat-transporting fluid, constructed as pipeline 72 , a heat-exchanger arrangement 74 , here with two rows, and also a pipeline of a drain arrangement for the heat-transporting fluid, which is here constructed as a collecting line and is provided with insulation 70 .
  • the heat-exchanger arrangement 74 has two rows 75 of spirals 53 arranged one behind the other, as illustrated in FIG. 5 .
  • the fluid passes through the line 72 at the inlet temperature T E to the connecting pieces 57 and as a result into each coil 53 , passes through the same and leaves the same via the end sections 58 of the pipeline 52 at the outlet temperature T A and thus passes into the pipeline 25 of the drain arrangement.
  • secondary concentrators 73 known to the person skilled in the art as trumpets, which run along the thermal openings 59 over the length L of the absorber arrangement 61 in a suitable manner and thus concentrate the radiation already concentrated by the concentrators 62 , 63 in the transverse direction of the trough collector a second time in the transverse direction, which makes it possible to reduce the width of the thermal openings.
  • Frame and structure elements 71 support the arrangement shown in the figure and can be constructed suitably in an actual case by the person skilled in the art.
  • a number of absorber spaces lying one behind the other in a row is provided over the length of the absorber arrangement, which absorber spaces are arranged separated from one another at a distance from one another.
  • Such an embodiment is advantageous if the radiation reflected by at least one concentrator ( FIG. 1 ) or by a plurality of concentrators 62 , 63 ( FIG. 6 ) is concentrated longitudinally upstream of the absorber arrangement by a further arrangement of longitudinal concentrators, so that instead of a focal line region, a number of focal point regions (wherein one or a plurality of longitudinally extending rows of focal point regions are possible) are present with greater concentration.
  • Coils modified compared to the coils 53 shown in FIG. 5 are likewise compliant with the invention. These may for example form an elliptical or polygonal absorber space instead of a round one, or be terminated at the wall opposite the thermal opening with a simple lid in the place of the coils of the pipe 52 shown in FIG. 5 . (Likewise, the absorber spaces may for example consist of one box in each case in the place of the spaces formed by lines).
  • coils the axis of symmetry of which is inclined with respect to the thermal opening (and not perpendicular according to the illustration in FIG. 5 ), with the advantage that such coils are advantageous for a skew angle range.
  • the skew angle is known as such to the person skilled in the art and designates the angle at which the sun falls onto the concentrator orientated towards it.
  • the heat-exchanger arrangement and thus the at least one absorber space can be adapted and configured in terms of design in accordance with the thermodynamic requirements present in the actual case, but the heat-exchanging fluid is heated in the transverse flow to operating temperature, i.e. to the outlet temperature T A , so that the drain arrangement is fed fluid at the outlet temperature A T at the length L thereof.
  • the heat-exchanger arrangement may not only be formed by pipelines, but rather also by means of another suitable construction.
  • each segment has a connection for a fluid source.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Sustainable Energy (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Sustainable Development (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Dispersion Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Loading And Unloading Of Fuel Tanks Or Ships (AREA)
US14/409,400 2012-06-24 2013-06-20 Absorber arrangement for a trough collector Abandoned US20160040909A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
CH895/12 2012-06-24
CH00895/12A CH706688A1 (de) 2012-06-24 2012-06-24 Absorberanordnung für einen Rinnenkollektor.
CH00899/12A CH706691A2 (de) 2012-06-24 2012-06-25 Absorberanordnung für einen Rinnenkollektor.
CH899/12 2012-06-25
PCT/CH2013/000109 WO2014000114A2 (de) 2012-06-24 2013-06-20 Absorberanordnung für einen rinnenkollektor

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US20160040909A1 true US20160040909A1 (en) 2016-02-11

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US14/409,400 Abandoned US20160040909A1 (en) 2012-06-24 2013-06-20 Absorber arrangement for a trough collector

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US (1) US20160040909A1 (es)
EP (1) EP2864717A2 (es)
JP (1) JP5890067B2 (es)
KR (1) KR20150021939A (es)
CN (1) CN104541112A (es)
AU (1) AU2013284276A1 (es)
CH (2) CH706688A1 (es)
CL (1) CL2014003427A1 (es)
IL (1) IL236255A0 (es)
IN (1) IN2014DN10867A (es)
MA (1) MA37660B1 (es)
MX (1) MX2014014714A (es)
TN (1) TN2014000525A1 (es)
WO (1) WO2014000114A2 (es)
ZA (1) ZA201409352B (es)

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US8069849B2 (en) * 2009-02-13 2011-12-06 Matalon Energy, Llc Parabolic solar collector
CN201828043U (zh) * 2010-09-21 2011-05-11 广东工业大学 集热、储热及供热一体化槽式太阳能中高温热利用装置
CN102135331A (zh) * 2011-03-16 2011-07-27 北京航空航天大学 一种槽式太阳能集热器

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AU2013284276A1 (en) 2015-01-22
CL2014003427A1 (es) 2015-02-27
ZA201409352B (en) 2015-12-23
MA37660A1 (fr) 2016-01-29
MA37660B1 (fr) 2016-08-31
CN104541112A (zh) 2015-04-22
MX2014014714A (es) 2015-03-06
JP5890067B2 (ja) 2016-03-22
CH706691A2 (de) 2013-12-31
WO2014000114A2 (de) 2014-01-03
CH706688A1 (de) 2013-12-31
EP2864717A2 (de) 2015-04-29
KR20150021939A (ko) 2015-03-03
WO2014000114A3 (de) 2014-06-19
JP2015520357A (ja) 2015-07-16
IL236255A0 (en) 2015-02-26
IN2014DN10867A (es) 2015-09-11
TN2014000525A1 (en) 2016-03-30

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