Classifications

• • 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
  • 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 according to the preamble of claim 1.
• Solar tower power plant systems have a central, raised (on the "tower") mounted absorber for hundreds to thousands of individual mirrors with mirrored to him sunlight, so that the radiation energy of the sun over the many mirrors or concentrators point concentrated in the absorber and due to the achievable high concentration temperatures up to 1300 ° C can be achieved, which is favorable for the efficiency of the downstream thermal machines (usually a steam or fluid turbine power plant for power generation).
• Solar tower power plants have (despite the achievable ho- hen Temperatures) because of their own, sometimes difficult technology until now also found no wider distribution.
• parabolic trough power plants are widespread and have trough collectors which have long concentric transducers with small transverse dimensions, and thus have not a focal point but a focal line, which fundamentally differentiates them in their design from the Dish Sterling and solar tower power plants.
• These line concentrators today have a length of 20 m to 150 m, while the width can reach 5 m or 10 m and more.
• a absorber line for the concentrated heat up to 500 ° C
• the absorber line is flowed through by a medium that absorbs the heat and transported via a pipeline network to the powerhouse of the power plant.
• a heat-transporting medium is a fluid such. Thermal oil or superheated steam in question.
• the aim is to increase the temperature in the heat-transporting medium as much as possible, since with its higher temperature, the conversion efficiency of the heat generated in the power plant in, for example, electricity is higher.
• the highest possible temperatures are also targeted if the solar power plant is to supply process heat for industrial production.
• heat losses For the efficiency of the power plant but also the emission or radiation of heat through the pipe network (heat losses) is to be considered, in which the heat-transporting medium circulates. This can reach 100 W / m, with a line length in a large system up to 100 km, so that the heat losses via the pipeline network are of considerable importance for the overall efficiency of the power plant, so that the air flows onto the absorber tubes. falling share of heat losses. From the above information it follows that the entire length of the trough collectors and correspondingly also that of the absorber tubes in such solar systems reaches tens of kilometers, thus their heat losses for the efficiency of the entire system can not be neglected.
• the absorber lines are increasingly expensive to avoid such energy losses.
• widespread conventional absorber lines are formed as a metal tube encased in glass, wherein there is a vacuum between glass and metal tube.
• the metal tube carries in its interior, the heat-transporting medium and is provided on its outer surface with a coating that absorbs irradiated light in the visible range improved, but has a low radiation rate for wavelengths in the infrared range.
• the enveloping glass tube protects the metal tube from cooling by wind and acts as an additional barrier to heat dissipation.
• the disadvantage here is that the enveloping glass wall also partly reflects or absorbs incident concentrated solar radiation, which results in a reflection-reducing layer being applied to the glass.
• the absorber line can be lent addition to a surrounding mechanical protective tube, which must be provided with an opening for the incident solar radiation, the Absorber line but otherwise quite reliable protection.
• WO 2010/078 668 (which is hereby incorporated by reference in the present application) discloses an improved-efficiency outer-insulated absorber tube whose elongated thermal opening, formed as a slot opening by use in a trough collector, is optimized in terms of heat losses, in that the thermal opening is reduced over the length of the absorber tube, in accordance with the increasing temperature over the length of the medium transporting the absorber tube from the longitudinally flowing heat. As the heat radiation increases with the fourth power of the temperature is so avoided a major part of the total energy losses of the absorber tube, although the costly measures for the reduction of the thermal opening are made only in a relatively small portion of the absorber tube.
• the object of the present invention is to provide an absorber arrangement suitable for high operating temperatures of the heat-absorbing medium, which has low heat losses and can be produced inexpensively in series.
• a heat exchanger assembly which is designed for the flow of the heat-transporting fluid in the cross-flow, can be formed on the separation of the at least one absorber space from the fluid-carrying heat exchanger, the absorber space such that even at high temperatures of more than 500 ° C, for example to 650 ° C or even higher, the heat radiation is reduced by its thermal opening reduced, thereby the efficiency of the heat exchanger assembly is improved as a whole.
• FIG. 2 shows a view of a section of a first embodiment of the absorber arrangement according to the invention
• FIG. 3 shows a view of a section of a second embodiment of the absorber arrangement according to the invention
• FIG. 4 shows a view of a section of a third embodiment of the absorber arrangement according to the invention
• 5 shows a view of 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 longitudinally extending absorber chambers arranged parallel to one another, and
• FIG. 7 shows a cross-section through the absorber arrangement of FIG. 6.
• FIG. 1 shows a trough collector 1 of a conventional type, with a concentrator 2 which is parabolically curved in cross-section and reflects incident solar rays 3, the reflected rays 4 being concentrated in a focal zone, in which an absorber tube 5 is arranged.
• the absorber tube 5 Via a feed line 6, the absorber tube 5 is charged with a heat-transporting medium, which flows through it, thereby heated from an input temperature T E to an output temperature T A and finally discharged through a discharge line 7.
• the course of the temperature T of the heat-transporting medium over the length L of the absorber tube 5 is qualitatively represented by the curve 15.
• the temperature curve 15 is substantially linear, corresponding to the uniformly over the length L by the reflected rays 4 the absorber tube 5 (and thus the longitudinally flowing through this fluid) supplied heat.
• the absorber tube 5 has a thermal opening, not shown for relieving the figure, through which the rays reach the interior of the absorber tube 5 and heat the heat-transporting fluid.
• a thermal opening not shown for relieving the figure, through which the rays reach the interior of the absorber tube 5 and heat the heat-transporting fluid.
• Such an arrangement is known to the person skilled in the art, for example from the abovementioned WO 2010/078 668.
• the interior of the absorber tube 5 (including the heated heat-transporting fluid) heated by the reflected beams 4 radiates in the infrared zone.
• Rarot Scheme heat wherein this heat-return or remission escapes through the thermal opening of the absorber tube. This reflection or remission increases with the fourth power of the temperature prevailing in the interior of the absorber tube 5.
• the curve 16 qualitatively shows the course of the radiation intensity through the thermal opening of the absorber tube 5.
• the absorber tube continuously loses energy with the fourth power of its internal temperature, so that a basically desirable further increase in the starting temperature T A from 500 ° C to, for example, 650 ° C or more, among other things problematic because the reflection or remission after a certain length of the absorber tube 5 is the same height as the irradiation by the reflected beams 4, so that a further increase in the temperature Fluid no longer takes place.
• Figure 2 shows schematically an absorber assembly 20 according to the present invention, as it can be used in place of the absorber tube 5 in a trough collector 1 ( Figure 1). Only one longitudinal section 21 of the absorber arrangement 20 is shown in the figure, beginning with a cross section through the absorber arrangement 20 at an arbitrary position along its length and a view of the longitudinal section 21 following the cross section up to a section line 22, wherein the absorber assembly 20 continues after the cutting line 22 to the end of the respective trough collector.
• absorber arrangements can be realized in a length greater than 100 m, preferably greater than 150 m and preferably up to 200 m or more, which allows correspondingly long trough collectors and for the industrial use of trough collectors in a solar power plant is cheap.
• the pipes 26 are here next to each other in two rows 27 and 28 and form a heat exchanger assembly 29.
• the row 28 is indicated by the contours of the juxtaposed pipes 26, the row 27 is hidden in the view shown.
• Between the rows 27, 28 of pipes 26 of the heat exchanger assembly 29 is an absorber space 30 for concentrated, ie reflected radiation 4, through the thermal opening 35, the beams 4 are incident. Walls 36 of the absorber space 30 absorb the heat of the heat incident on the beams 4 and deliver them to the conduits 26 of the heat exchanger assembly 29 with which they are thermally connected, for example by direct contact with the walls 36, as shown in the figure is shown.
• heat transporting fluid is supplied through inlet sections 38 from conduits 23,24 of the supply line to conduits 26 of heat exchanger assembly 29 over the length L at the inlet temperature T E , wherein the fluid in the conduits 26 is heated to the outlet temperature T A and is discharged at this temperature from the output sections 39 to the pipe 25 of the discharge arrangement, also over the length L of the absorber arrangement.
• the supply line arrangement and the discharge line arrangement have a supply pipe 23, 24 and a discharge pipe 25, wherein the pipes 23, 24, 25 run parallel to one another and the at least one absorber space 30 is arranged between pipes 23, 24, 25 and extends over the length of the tubes 23,24,25.
• the feed arrangement comprises a supply line 23,24 extending over the length of the absorber assembly for the heat exchanger to be heated over its length to be heated, the feed line 23,24 preferably over its length except for the feed openings the heated fluid is thermally insulated. This can be advantageous if the input temperature T E is above the ambient temperature.
• the discharge arrangement the length of the absorber assembly along extending manifold 25 has for its over its length from the heat exchanger assembly 29 forth supplied heated fluid, wherein the manifold 25 along its length except for the openings for the supply of the heated fluid is thermally insulated.
• the heat-transporting fluid still flows longitudinally through the absorber arrangement, but in two separate streams, once with the inlet temperature T E and once with the output temperature T A , as symbolized by the flow arrows in the figure. Furthermore, it follows that the heat-transporting fluid is moved transversely to the length of the absorber arrangement during the absorption of heat. In the heat exchanger arrangement, however, the fluid flows in cross-flow to the length L, with the result that over the entire length L of the absorber arrangement 20 in the line 25 of the discharge arrangement fluid with the Knoxtermatur T A is present.
• the absorber space 30 can be designed in such a way by the person skilled in the art that, in the case of a given concentrator 2 (FIG.
• the thermal opening 35 "sees" predominantly the entrance area with regard to the reverberation, but far less the wall (far away, rearmost) of the absorber space 30, which in turn is heated to the starting temperature T A It should be noted here, of course, that in all the embodiments according to the invention it may be advantageous to close the thermal opening by, for example, glass in order to reduce the heat return / re-emission.
• the person skilled in the art can achieve that the heat exchanging surface becomes large.
• the entire inner surface of the pipes 26 of the heat exchanger assembly serves as a heat exchanging surface.
• the heat conduction in the material of the pipelines 26 for example, a good heat conductive material such as copper or a suitable, good heat conducting alloy at high temperatures
• the pipes 26, however heat almost uniformly all around, so that the heat exchanging surface is correspondingly large.
• a large heat exchanging surface serves the efficient heat transfer to the heat transporting fluid, so that a local overheating of the heat exchanging surface can be largely avoided.
• the walls heated by the radiation often overheat, with the result that the reflection / emission is massively increased.
• the reason for this lies in the longitudinal flow of the fluid to be heated, which in the high-temperature region of the conventional absorber tube, the heat-exchanging walls is already strongly heated itself, therefore, during the short time in which it flows through the end, whose walls can not cool enough. (An increase of the mass flow is not possible, since this must reach its target temperature T A for a given heat input by the reflected radiation 4. If the mass flow were increased, this temperature could no longer be reached).
• the absorber arrangement according to the invention although over its length L, there is a heat return / re-emission through the thermal opening 35 corresponding to the output temperature T A.
• the energy losses in the absorber arrangement according to the invention are, on the whole, lower than in the conventional absorber tube. Accordingly, the absorber arrangement in almost any length L can be performed without this would have negative consequences in terms of heat radiation.
• the dormitortermperatur the T A is reduced corresponding heat reflection in comparison with a conventional absorber tube as relevant by the geometry of the absorber chamber parts of the heat reflective or heat re-emitting walls are kept cool.
• the relevant wall regions of the absorber chamber located near the thermal opening remain cooler and overheating of the heat exchanging surfaces is substantially reduced compared to a conventional absorber tube.
• thermal opening can be used to designate a physical opening to the absorber space according to FIG. 2, depending on the design of the absorber tube.
• thermal opening also includes in other types of absorber space a physically closed area, which is designed for the heat transfer of concentrated solar radiation, for example, by suitable coatings at the site of heat radiation, a return of heat can be reduced.
• the person skilled in such constructions are known. Nevertheless, it is necessarily the case that at the location of the thermal opening ultimately no good insulation can be achieved, so the corresponding relevant heat losses must be accepted by heat radiation / Reeimssion.
• the absorber arrangement according to the invention can only be used in a trough collector at a short distance from its edge, for example after the fluid has reached a temperature of 100 ° C. or slightly more. However, an absorber arrangement extending over the entire length of the trough collector according to the present invention is preferred.
• the pipes 26 of the heat exchanger arrangement 29 according to the invention can at least partially replace the walls of the absorber space 30, with the advantage that the pipes 26 are directly irradiated thereby, ie the heat transfer to the heat-transporting fluid is only minimally hindered.
• at least sections of the wall of the at least one absorber space are also formed by the heat exchanger or its pipelines. It is also according to the invention that the heat exchanger has adjacent line sections for the fluid, which form at least one wall section for the at least one absorber space.
• the absorber space can be formed by lines 42 of the heat exchanger assembly, as they extend in adjacent turns and so preferably completely envelop the interior of the absorber space.
• FIG. 3 shows a further embodiment of the absorber assembly 40 according to the present invention, which basically corresponds to that of Figure 2, with the exception of the formation of the heat exchanger assembly 41, which formed as pipes 42 lines laid here in small loops, so each longer.
• the heat exchanging fluid flows through the heat exchanger assembly 41 in cross-flow with respect to the longitudinal direction L.
• the tube 24 (FIG. 2) is omitted in FIG. 3 to allow the view of the pipelines 42.
• Longer pipes 42 have the advantage that the heat exchange surface for the flowing partial flow of the fluid increases, but the disadvantage that the pressure drop in the pipe 42 is greater.
• the person skilled in the art can suitably determine the flow and thermodynamic design of the pipelines 42.
• any suitable guidance of the heat-transporting fluid through the heat exchanger arrangement is according to the invention as long as it passes through the heat exchanger arrangement in its main direction transversely to the length L, such that the fluid heats up from an inlet temperature to the operating temperature in cross-flow operation and under this reaches the derivative arrangement.
• any suitable design of lines in the heat exchanger arrangement according to the invention is provided which serves for the flow of the fluid according to the invention.
• the small flow arrows 44 indicate the flow direction of the heat-transporting fluid.
• FIG 4 shows yet another embodiment of an absorber assembly 50 according to the present invention, which basically corresponds to that of Figure 2, again with the exception of the heat exchanger assembly 51, which are formed here as pipes 52 lines are laid in coils 53, that are each formed even longer.
• the coils 53 are indicated only schematically in the figure and shown in Figure 5 in detail.
• the spirals 53 formed from the pipes 52 are open at the bottom and thereby form absorber chambers 54, since a space section is enclosed by them. As a result, the heat exchanging surface for this space section and thus also over the length of the absorber arrangement 50 increases considerably, with the advantages mentioned above for FIG.
• the lower open areas of the coils 53 form thermal openings 59.
• the absorber chambers 54 are due to the arrangement of the coils 53 shown in a row 55. Also in Figure 4, the pipe 24 is omitted to relieve the figure, so that the view of the coils 53 is free. It can be seen that in the embodiment shown in the figure, the absorber arrangement 50 is designed such that the supply arrangement and the discharge arrangement have a supply pipe 23, 24 and a discharge pipe 25, the pipes 23, 24, 25 running parallel to one another and the here numerous, each formed by a spiral 53 Absorberhoff- me between these tubes 23 to 25 are arranged and extend over the length of the absorber assembly 50.
• FIG. 5 shows a view of one of the spirals 53 indicated only schematically in FIG. 4, formed from the turns of a line 52 of the inventive heat exchanger arrangement 51 formed here as a pipeline 52.
• the helix 53 here has an axis of symmetry 55 and encloses an absorber space 54 for the incident Radiation 4, wherein the bottom open end of the coil 53 forms a thermal opening 59.
• FIG. 4 shows an absorber arrangement in which the supply line arrangement and the discharge line arrangement have a feed pipe 23, 24 and a discharge pipe 25, wherein the pipes 23, 24, 25 run parallel to one another and a number of absorber spaces 54 are provided, which in FIG at least one extending between these tubes 23,24,25 series 55 are arranged, wherein the at least one row 55 extends over the length of the tubes.
• FIG. 4 shows an absorber arrangement in which the supply line arrangement and the discharge line arrangement have a feed pipe 23, 24 and a discharge pipe 25, wherein the pipes 23, 24, 25 run parallel to one another and a number of absorber spaces 54 are provided, which in FIG at least one extending between these tubes 23,24,25 series 55 are arranged, wherein the at least one row 55 extends over the length of the tubes.
• 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 designed, for example, according to WO 2010/037 243 (which is incorporated herein by reference into the present application).
• the frame of the trough collector 60 is designed, for example, according to WO 2009/135 330.
• the absorber arrangement 61 has at least two absorber chambers 64 and 65, which extend over the length L of the absorber arrangement 61.
• FIG. 7 shows a cross-section through the absorber arrangement 61 of FIG. 6.
• a line 72 designed as a supply line arrangement for heat-transporting fluid, here a double-row heat exchanger arrangement 74 and a manifold 25 designed as a piping discharge arrangement for the heat-transporting fluid with an insulation 70 is provided.
• the heat exchanger assembly 74 has in the illustrated embodiment, two rows 75 of successively arranged coils 53, as shown in Figure 5.
• the fluid passes through the line 72 with the inlet temperature T E to the nozzle 57, thereby into each coil 53, flows through it and leaves it via the end portions 58 of the pipe 52 to the outlet temperature T A and thus enters the Pipe 25 of the discharge arrangement.
• Frame and structural elements 71 support the arrangement shown in the figure and can be made suitable by the skilled person in the specific case.
• a number of absorber spaces lying behind each other in a row are provided over the length of the absorber arrangement, which are arranged separately from one another at a distance from each other.
• Such an embodiment is advantageous if the radiation reflected by the at least one concentrator (FIG. 1) or by a plurality of concentrators 62, 63 (FIG. 6) is longitudinally concentrated in front of the absorber arrangement by a further arrangement of longitudinal concentrators, so that instead of a focal line region a number of focus areas (one or more being longitudinal extending rows of focal areas are possible) with increased concentration.
• modified turns are also provided in relation to the helix 53 shown in FIG.
• These may, for example, instead of a round form an elliptical or angular absorber space, or be closed at the opposite wall of the thermal opening with a simple cover instead of the turns of the tube 52 shown in Figure 5.
• the absorber rooms may, for example, each consist of a box instead of the spaces formed by lines).
• helixes whose symmetry axis is inclined with respect to the thermal opening (and not perpendicularly as shown in FIG. 5) have the advantage that such helixes are advantageous for a skew-angle range.
• the skew angle is known to those skilled in the art and refers to the angle at which the sun is incident on the concentrator aligned therewith.
• the heat exchanger arrangement and thus the at least one absorber space can be adapted and designed constructively by the person skilled in the art according to the thermodynamic requirements present in the specific case, but with the heat exchanging fluid in cross flow at operating temperature ie at the outlet temperature T. A is heated, so that the discharge arrangement is fed to its length L fluid with the output temperature T A.
• the person skilled in the art can, depending on the requirements in a specific case, combine the features explained in the various embodiments described above, since these are not bound to the respective embodiments shown.
• the heat exchanger assembly can be formed not only by piping, but also by another suitable construction.
• each segment has a connection for a fluid source. This reduces energy losses due to the pressure drop in a long line.

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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)

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• 2012
  • 2012-06-24 CH CH00895/12A patent/CH706688A1/de not_active Application Discontinuation
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• 2013
  • 2013-06-20 US US14/409,400 patent/US20160040909A1/en not_active Abandoned
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