WO2009043334A2 - Absorbeur d'énergie air-solaire - Google Patents

Absorbeur d'énergie air-solaire Download PDF

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Publication number
WO2009043334A2
WO2009043334A2 PCT/DE2008/001598 DE2008001598W WO2009043334A2 WO 2009043334 A2 WO2009043334 A2 WO 2009043334A2 DE 2008001598 W DE2008001598 W DE 2008001598W WO 2009043334 A2 WO2009043334 A2 WO 2009043334A2
Authority
WO
WIPO (PCT)
Prior art keywords
heat
air
supply device
heat supply
solar
Prior art date
Application number
PCT/DE2008/001598
Other languages
German (de)
English (en)
Other versions
WO2009043334A3 (fr
Inventor
Frank Schubert
Dirk Drews
Original Assignee
Solarhybrid Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Solarhybrid Ag filed Critical Solarhybrid Ag
Priority to DE112008003356T priority Critical patent/DE112008003356A5/de
Priority to EP08835769A priority patent/EP2198203A2/fr
Publication of WO2009043334A2 publication Critical patent/WO2009043334A2/fr
Publication of WO2009043334A3 publication Critical patent/WO2009043334A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/002—Central heating systems using heat accumulated in storage masses water heating system
    • F24D11/003—Central heating systems using heat accumulated in storage masses water heating system combined with solar energy
    • 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
    • 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
    • F24S20/00—Solar heat collectors specially adapted for particular uses or environments
    • F24S20/40—Solar heat collectors combined with other heat sources, e.g. using electrical heating or heat from ambient air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S70/00—Details of absorbing elements
    • F24S70/60—Details of absorbing elements characterised by the structure or construction
    • F24S70/65—Combinations of two or more absorbing elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/002—Machines, plants or systems, using particular sources of energy using solar energy
    • F25B27/005—Machines, plants or systems, using particular sources of energy using solar energy in compression type systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • F28D1/024—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels with an air driving element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/272—Solar heating or cooling
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/20—Solar thermal
    • 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 heat supply device for heating buildings with a solar collector for receiving solar energy.
  • the energy gained through the heat supply device can either be used directly for heating residential or office space or the heating of service water or indirectly via a heat pump, by transforming to a higher temperature level.
  • Thermal solar collectors are known in various embodiments. These are surface-mounted systems that expediently mount or set up outside buildings, absorb the direct solar radiation and convert the radiation and light energy into heat. The heat is transferred to pipeline-bound heat transfer media and is usually supplied to buffer storage tanks, in the form of larger water tanks, for the purpose of storing and distributing the recovered energy.
  • air heat pumps installed outside the building for heat generation are known for obtaining heat energy from the ambient air, which consist of units made up of fin heat exchangers with fans, compressors, water heat exchangers on the heat output side and fittings in a housing.
  • split system is also known in which the finned heat exchanger with fan and refrigeration fittings are housed in a separate housing for outdoor installation and the compressor with the remaining components are placed separately in another housing. Both units are connected by pipelines.
  • the finned heat exchanger can be flowed through directly by evaporating, latent heat receiving refrigerant or by a sensitive heat receiving medium such as water or brine.
  • the heat absorbed by the heat pump at low outside air temperatures and compressed by the compressor is transferred to buffer storage for buffer storage and distribution, or transferred directly to the structure, primarily in underfloor heating systems.
  • solar hybrid collectors are known, which are conventional flat thermal collectors, which in addition to the main function to absorb solar radiation energy through flat radiation absorbing elements are able, as an additional function, heat energy from the outside air by means of small ventilation systems during the low-irradiation operating times on the absorber surfaces and to accommodate the conventional existing hydraulic heat transport system.
  • the proportion of the drive energy to be applied is proportional to the overcoming temperature difference.
  • a 30% higher drive current is needed to transform a constant amount of heat from 25 ° C to 55 ° C than it would be for a system designed for these conditions.
  • thermal hybrid collectors described above are in the main function conventional thermal solar collectors with the disadvantages described.
  • the effectiveness of the additional function, the absorption of heat energy from the ambient air, is relatively low, so that hybrid collectors in day and seasonally low-irradiation periods can not work to cover heat demand, unless it disproportionately large areas are installed, which is economical and often architectural or structural boundaries.
  • thermal solar collectors with air heat pumps results in compact, efficient heat supply devices.
  • the strength of solar thermal systems namely the possibility of direct use of solar energy
  • drive of pumps can be gen amounts of drive energy (drive of pumps)
  • air heat pump systems namely the possibility of recovering heat energy in low-radiation times and at low outside temperatures, synergistically.
  • Day and seasonally different exploitation potentials of direct solar energy and outdoor air energy are used efficiently.
  • the solar collector forms an upper cover of the housing of the air heat pump, resulting in an upwardly rain-tight completion of the heat supply device and in particular an electrically operated fan of the laminated air heat exchanger of the air heat pump is covered and protected from external contaminants.
  • the solar collector envelops an upwardly closed airspace.
  • This airspace can be collected by the sun's warm air, whose energy can be harnessed.
  • the solar collector is an integral part of the housing of the air heat pump or is detachably connected to the housing of the air heat pump.
  • the heat supply device heat transfer fluid carrying pipelines for forwarding the heat absorbed by the solar collector, especially for aqueous solutions, glycol, etc.
  • the heat from the outdoor installed heat supply device by connecting to other pipelines in the building or in a buffer will be forwarded within the building.
  • the solar collector has an absorber surface and the pipelines run below the absorber surface or are formed as an integral part of the absorber surface, resulting in a favorable heat transfer from the absorber surface to the heat transfer fluid.
  • a surface of optically transparent material forming the outer skin of the solar collector be provided above the absorber surface.
  • the heat exchanger of the air heat pump has fins and the solar collector is embedded in the fins of the heat exchanger such that the surfaces of the fins form the absorber surfaces of the solar collector.
  • the heat exchanger which are held in particular in black color, not only serve to absorb the energy of these overflowing air, but at the same time to absorb the sun's rays impinging on them and thus to absorb solar energy.
  • the lamellae can therefore be operated either only as solar absorption surfaces, only as overflow lamellae, or in combined operation as a combination of both. Not all fins need serve as solar absorption surfaces. Depending on the angle of incidence of the sun, it is possible that certain slats or slats areas are not exposed to solar radiation. In this context, it is advantageous if the heat transfer medium-carrying pipelines of the solar collector run through the lamellae of the air heat exchanger, in particular transversely to the surface thereof.
  • the air heat pump has pipelines of a refrigerant circuit of a heat pump, which run through the fins of the air heat pump, in particular transversely to the surface thereof. These pipelines form the evaporator tubes of the heat pump process.
  • the fins of the air heat pump are surrounded by a transparent hood.
  • the transparent hood also has an important mechanical protective function, e.g. against vandalism, and meets the requirements regulated by standards and laws (Machinery Directive, CE).
  • the solar radiation passes through the hood on the serving as absorber surfaces fin surfaces.
  • hood has a distance from the slats, whereby a aufloomender under the influence of solar radiation in the manner of a greenhouse interspace arises.
  • the accumulating in this space heat is also made available on the surfaces of the finned heat exchanger and the running in the disk packs pipelines.
  • directly usable amounts of heat as in known solar collectors.
  • the air heat pump has an air inlet to the entry of ambient air, which is slit or lattice-shaped, so that coarse contaminants such as leaves or paper can not enter the interior of the heat supply device.
  • the air inlet can be closed, whereby an effective heat accumulation is achieved in the interior of the heat supply device. From the closure of the air inlet could continue to be used in the defrosting process of the finned evaporator, which in this case also causes a build-up of heat and thus accelerates the defrosting process and makes it possible for larger wind forces in the first place.
  • the heat released to the ambient air during defrosting (defrost loss heat) would be largely recovered when the normal heat pump function is resumed because it can not be dissipated by the outside air.
  • the pipes not belonging to the heat pump process form a closed circuit to which heat can be withdrawn via a heat exchanger.
  • the circuit carries heat transfer fluid, such as glycol, which is heated at the solar collector by heat transfer from the absorber surface, then fed to the heat exchanger, cooled there and then performed for reheating in the solar collector.
  • the heat released in the heat exchanger can be used to heat the building be made available, for example by storage in a buffer memory.
  • An embodiment is advantageous in which switching means are provided via which the heat exchanger can be switched out of the circuit under certain environmental conditions. This is the case, for example, when the solar temperature applied to the absorber surfaces falls below a level of about 40 ° C., since in this case the temperature of the heat transfer fluid would be too low for direct storage in the higher temperature buffer.
  • switching means are provided, by means of which the circuit with the refrigerant circuit of the heat pump can be coupled via a heat exchanger.
  • the heat is fed via a corresponding heat exchanger in the refrigerant circuit of the air heat pump, where it is transmitted via a compressor to the refrigerant of the refrigerant circuit of the air heat pump and is transferred there by means of a compressor to a higher temperature level.
  • At least one air temperature sensor, a solar temperature sensor and a storage level sensor are provided, which are connected to a control unit, which causes a changeover of the changeover means as a function of the detected temperatures, whereby an automatic adaptation of the heat supply device to the given environmental conditions and the heat demand in the buffer memory.
  • FIG. 1 is a perspective view of a heat supply device
  • FIG. 4a shows a further embodiment of a heat supply device in a perspective view
  • FIG. 4b is a representation corresponding to FIG. 4a with outbreaks to illustrate the internal structure of the heat supply device, FIG.
  • FIG. 5 shows a further embodiment of a heat supply device in a side view
  • FIG. 6 is a sectional view through the heat supply device according to FIG. 4a, b or FIG. 5, FIG.
  • FIG. 7 is a further sectional view through a heat supply device according to a further embodiment
  • 8 is a partial perspective view of a heat supply device according to another embodiment
  • FIG. 9 is a sectional view of the heat supply device of FIG. 8 and
  • FIG. 1 shows a heat supply device 100 according to the invention, in which an outside air heat pump 1 in a compact design or the outside part of an air heat pump in a split design are combined with a solar collector 2 in a structural unit.
  • air heat pump is therefore to be understood below as including both a complete air heat pump and the outer part of an air heat pump in split design.
  • the air heat pump 1 has a laminated air heat exchanger 1a, a fan 1b, and other not shown in Fig. 1 components, such as fittings, a housing, etc. on.
  • a roughly hemispherical designed solar collector 2 can be seen, which is designed as the upper Deckab gleich the heat pump housing of the air heat pump 1 and also serves as a shelter for the underlying fan 1b of the air heat pump 1.
  • the solar collector 2 installed on the heat pump 1 may be designed as an integral, i. integral, formed part of the heat pump housing or may be detachably mounted on the heat pump housing.
  • the solar collector 2 has an absorber surface 2 a as well as a plurality of spirally or helically running pipelines 2 b which are either located inside the absorber surface 2 a or in the radiation direction. seeks below the absorber surface 2a are arranged and serve to forward the received from the direct radiation or from the outside air heat energy.
  • the pipelines 2b are part of a heat transfer fluid, such as glycol, leading circuit K F , which will be explained in more detail below with reference to the illustration in FIG.
  • the solar energy receiving surface 2a can also be designed directly as a heat carrier leading element.
  • a light and radiation permeable hood or plate is mounted as impermeable to air as possible, so that warm air which collects below the hood can not escape upwards.
  • the design of the heat carrier lines or the pipes 2b is either in accordance with the requirements for aqueous solar liquids and / or refrigerant as evaporator tubes.
  • the heat supply device 100 has an air heat exchanger 1 in the cylinder design below the solar collector 2 designed as a hemispherical cover.
  • the designed as a cylindrical substructure air heat exchanger 1 is next to chassis and housing components from the outside, roller-shaped arranged laminated air heat exchanger 1a, the fan 1b, and possibly other technical components inside together.
  • the air heat pump 1 is characterized by a, formed by the fins, very large heat exchange surface, which may extend radially from the center of the cylindrical air heat exchanger 1a or in parallel alignment. Since the thermal energy content of the air is relatively low, large areas are required, which are covered by the outside air to technically meaningful heat gains for domestic heating and dhw to enable.
  • the air is for the purpose of said heat gain usually with one or more fans 1b conveyed mechanically over the slat air heat exchanger 1a and cooled by this.
  • the cooling of the air over the lamellae 1a is done by the evaporation of a boiling refrigerant in the pipelines thereof, which are not shown in Fig. 1.
  • the same effect can be achieved by the guidance of a cooled under the temperature of the outside air aqueous heat transport medium in the pipes of the fin exchanger 1b.
  • the heat gained is, as already described, brought to a useful, higher temperature level with the aid of a compressor.
  • the hemispherical attachment is technically similar to a conventional solar flat collector.
  • the shaping outer skin consists of translucent material such as glass, Plexiglas or acrylic glass.
  • the actual absorber surface 2a for the absorption of the radiation energy of the sun is arranged at a certain distance in the air-sealed space.
  • the absorber surface 2a is usually colored in black and consists of material which promotes the absorption of energy.
  • a piping system 2b is fixedly connected to the absorber surface 2a. In the pipes 2b moves a heat transfer medium which the absorber surface 2a removes the heat.
  • the heat transport medium is in conventional solar collectors usually an aqueous salt solution or a water mixture which is enriched with antifreeze.
  • the absorbed heat is forwarded by the heat transfer medium to other components, eg buffer storage, by means of a hydraulic system. It follows that the temperature level of the heat transfer medium must be higher than the temperature of the storage water of the possible buffer storage, as the recipient of the storage meenergy to use heat according to the laws of physics. This means that in conventional solar collectors only amounts of heat with temperatures generally in the majority well above 45 0 C can be used.
  • the invention described here is characterized in that in addition to the conventional direct use of solar energy and the heat gained by the solar collector can be used at a temperature of 45 0 C. This is done by transforming the thermal energy absorbed by the solar collector with the help of the heat pump process according to the known thermodynamic principles to a higher temperature level. Said pipelines 2b can lead directly as conventional aqueous mixtures or solutions or evaporating refrigerant of the heat pump process. The latter significantly increases the efficiency of the heat pump process. It is possible according to the invention that the absorber surface 2a is equipped with a hybrid pipe system, wherein a hydraulic pipe system and a refrigerant system according to the Carnot process or as a heat pipe system (heat pipe) can be paired.
  • FIG. 2 shows possible geometrical modifications of the solar collector 2, which according to variant v2a may be cylindrical, conical in accordance with variant v2b and cubic in variant v2ac.
  • 3 shows possible geometric modifications of the air heat pump 1, which according to the variant can be cubic with a V-shaped arrangement of the lamellae, according to variants v1b and v1c can be cubic with vertically arranged lamellae, whereby one or more fans 1b are provided in each case could be.
  • FIGS. 4a, b Another embodiment of the invention is shown.
  • the heat absorbed by the absorption of the solar radiation is transferred to the heat transfer fluid-carrying pipe 2b of the solar collector 2, which extends through the fins 9 therethrough, and dissipated.
  • the heat energy transferred to the heat transfer fluid of the pipeline 2b is transferred to the ambient air by the flow around the fins 9.
  • This heat transfer fluid is an aqueous salt solution or a water mixture.
  • the pipes 2c of the refrigerant circuit required for the operation of the air heat pump 1 are also contained in the fins 9, in which a refrigerant boiling at low temperatures is conducted.
  • the pipes 2b and 2c are parallel to each other and pass vertically through the surfaces of the fins 9 therethrough.
  • the lamellae 9 are arranged in an annular shape in an oblong shape in a radial orientation, resulting in an overall hollow cylindrical structure, in the center of which the ventilator 1b is arranged. In contrast to the embodiment of FIG.
  • the fan 1b in which the fan 1 b is arranged above the slats and the air is conveyed from top to bottom by generating an overpressure on the slats, the fan 1b generates in the embodiment of FIG. 4, a negative pressure , via which the ambient air is conveyed via the fins 9.
  • the compressor 7 can also be seen, through which the refrigerant guided in the pipes 2c compressed and thus can be transformed in a heat pump process to a higher temperature level.
  • a hood 3 made of transparent material, such as glass, Plexiglas or similar materials, which is slipped over the solar collector 2 and the fins 9 of the Heilmér- mepumpe 1.
  • the hood 3 has a distance a with respect to the slats 9, so that an annular space 4 is formed, which heats up under the influence of solar radiation in the manner of a greenhouse.
  • the available in the space air heat passes through the fins 9 and in the area between the fins 9 directly on the pipes 2b and 2c and thus on the guided in these media over.
  • an air inlet 5 is provided, via which air from the environment enters the interior of the hood 3 and, due to the negative pressure generated by the fan 1b, is guided over the surface of the lamellae 9.
  • a baffle 18 is provided, which initially deflects the incoming air tangentially into the annular space 4, from where they then radially corresponding to the generated in the center of the arrangement on the fan 1b negative and is conveyed downwards along the surface of the lamellae 9, cf. Fig. 6.
  • FIG. 7 shows a symmetrical arrangement of two, opposing air inlets 5.
  • the air inlet 5 is provided with roller blind or blind-like closing elements 10, via which the air inlet 5 can be closed.
  • the arrangement of closing elements is functionally not required, but improves the performance.
  • the air inlet 5 should at least be provided with a weather protection grid.
  • the provided in the lower part of the heat supply device Luftaus- outlet 11 with lamellar elements designed as weather protection.
  • the air outlet may be provided with closing elements 10.
  • the air inlet 5 may be provided with a mesh screen as a filter element against coarse impurities carried in the intake air flow.
  • the solar collector 2 is arranged not only in the region of the fins 9 of the air heat exchanger 1, but the solar absorption surface is by a hemispherical solar collector region 19, which in turn forms a top cover of the housing 24 of the air heat pump 1 similar to the representation in FIG.
  • the pipes 2b passing through the fins 9 are flow-connected to the pipes 2b of the solar collector region 19.
  • the conduits 2b carrying the aqueous heat transfer fluid form a closed circuit K F.
  • the circuit KF leads in the manner shown in Figures 4 to 9, which is shown in Fig. 10 simplified for reasons of clarity, driven by the fins 9 and the absorber section 19 via a pump 20 to a heat exchanger 12.
  • the heat exchanger 12th it is a multiple heat exchanger, such as a multi-plate heat exchanger.
  • the heat transfer fluid transfers its heat to a useful water circuit KN, via which the heat is then fed via a pump 22 to a buffer storage 21, from which the heat is available for heating the building or for heating process water stands.
  • the subsequently cooled heat transfer fluid passes back into the heat supply device 100 and passes through the fins 9 and the absorber section 19 again.
  • the above-described mode of operation is always used when the heat absorbed by the solar radiation is at a temperature level which is sufficient for feeding into the buffer memory 21.
  • This temperature can be assumed, for example at 40 ° C. If the temperature applied to the solar absorption surfaces falls below the value of, for example, 40 ° C., the temperature is lower than that of the buffer store 21, so that it is not possible to feed the heat absorbed by the solar cycle KF directly into the latter.
  • switching means 13 are therefore provided which deflect the course of the heat transfer fluid conducted in the pipes 2b in such a way that it is no longer guided through the heat exchanger 12.
  • the deflection of the heat transfer fluid flow in the pipes 2b below a solar temperature of for example 40 0 C can be done in different ways depending on the temperature of the ambient air, which will be explained below.
  • the heat-transfer fluid flowing in the pipelines 2b absorbs heat in particular in the area of the collector section 19, in which ambient air heated by solar radiation accumulates on the sections of the tubes 2b extending in this area.
  • the heat absorbed there is then supplied to the refrigerant circuit K ⁇ of the air heat pump 1 when passing through the fins 9 via the fins 9.
  • the flow of the heat transfer fluid in the pipelines 2b is deflected via the changeover element 13 in accordance with the course shown in dotted lines in FIG.
  • the heat absorbed in the heat supply device 100 is supplied via a heat exchanger 17 to the refrigerant circuit KK. This mode of operation also comes into consideration in heat supply devices 100 with lamellae exposed and thus exposed to the wind.
  • the circuit K ⁇ is a heat pump cycle in which a refrigerant in the pipe sections of the fins 9 evaporates or boils when the ambient air flows over, then compressed via a compressor 23 and thus to higher temperatures is brought, then sufficient to charge the buffer memory 21 via the heat exchanger 12.
  • the switching of the switching means 13 is fully automatic, including solar temperature sensors 14 determine the temperature of the solar radiation absorbing surfaces of the solar collector 2 and air temperature sensors 15 are operatively connected to detect the ambient air temperature via a control element 16 with the switching means 13. Furthermore, the energy level in the buffer memory is monitored by the control technology as a criterion for triggering a changeover. Secondarily, a number of other measurement data are permanently evaluated in order to always set an economically favorable operating mode.
  • the inventive arrangement of the various system components allows a good utilization of the natural potential of direct solar energy and outdoor air energy in a compact design device.
  • the outdoor air heat pump 1 provides the required heat energy.
  • the air heat pump 1 is effectively relieved by the additional gain of solar heat.
  • additional refrigerant evaporation in the solar collector 2 this is over-cooled relative to the ambient air. Due to the self-adjusting temperature difference, on the one hand heat from the ambient air is absorbed and on the other hand the existing radiation supply is used in a technically meaningful way. The supercooling of the collector surfaces results in a higher negative radiation potential.
  • the outside air may have a temperature of 7 ° C which sets a possible evaporation temperature of the Carnot process of -3 0 C.
  • the supply of the heat obtained in the solar collector 2 raises the evaporation temperature and thus the efficiency of the heat pump process significantly, for example to 1 0 C.
  • the above-described state of hybrid use of both subsystems is to be found over a large part of the annual operating times.
  • the supply time and the energy yield of the thermal solar system with the support of the heat pump extended and on the other hand the efficiency of the air heat pump is effectively increased by means of the solar system.
  • Another advantage of the invention is the possibility of direct solar use of solar radiation.
  • the recovered heat energy is passed on directly to the buffer storage tank or to other energy consumers by means of control technology by means of a heat transfer medium. This only requires the energy of the circulation pumps. The expensive energy for driving the compressor is thus eliminated with sufficiently high solar power.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Sustainable Energy (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Dispersion Chemistry (AREA)
  • Photovoltaic Devices (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Central Heating Systems (AREA)

Abstract

L'invention concerne un dispositif d'alimentation thermique pour le chauffage de bâtiments, comprenant un capteur solaire (2) pour l'absorption de l'énergie solaire, dispositif caractérisé en ce qu'il comprend, sous forme d'une unité structurelle, une pompe à air-chaleur (1) pour l'absorption de l'énergie thermique provenant de l'air ambiant, connectée avec le capteur solaire (2).
PCT/DE2008/001598 2007-10-03 2008-10-03 Absorbeur d'énergie air-solaire WO2009043334A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112008003356T DE112008003356A5 (de) 2007-10-03 2008-10-03 Solarluftenergieabsorber
EP08835769A EP2198203A2 (fr) 2007-10-03 2008-10-03 Absorbeur d'énergie air-solaire

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202007013848.2 2007-10-03
DE202007013848 2007-10-03

Publications (2)

Publication Number Publication Date
WO2009043334A2 true WO2009043334A2 (fr) 2009-04-09
WO2009043334A3 WO2009043334A3 (fr) 2009-09-24

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PCT/DE2008/001598 WO2009043334A2 (fr) 2007-10-03 2008-10-03 Absorbeur d'énergie air-solaire

Country Status (3)

Country Link
EP (1) EP2198203A2 (fr)
DE (1) DE112008003356A5 (fr)
WO (1) WO2009043334A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202010001134U1 (de) * 2010-01-20 2010-06-24 Moser, Peter Kombination aus fassadenmontierten Solar-Luft-Kollektor mit integrierter Luft-Wärmepumpe
WO2011028186A3 (fr) * 2009-09-04 2011-04-28 Marko Matkovic Appareil frigorifique solaire thermique domestique
WO2013176611A1 (fr) 2012-05-21 2013-11-28 Värmestugan Ab Agencement de chauffage permettant de chauffer un fluide grâce à un panneau solaire

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060162720A1 (en) 2005-01-24 2006-07-27 Air Hydronic Product Solutions, Inc. Solar and heat pump powered electric forced hot air hydronic furnace

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2398980A1 (fr) * 1977-07-25 1979-02-23 Comp Generale Electricite Dispositif de chauffage utilisant le rayonnement solaire et la chaleur atmospherique
US4261329A (en) * 1979-07-25 1981-04-14 Walsh David P Multi-transport modular solar energy system
DE3444117A1 (de) * 1984-12-04 1985-05-09 Hans Dipl.-Ing. 7320 Göppingen Ruppert Sonnen- und luftkollektor fuer waermepumpen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060162720A1 (en) 2005-01-24 2006-07-27 Air Hydronic Product Solutions, Inc. Solar and heat pump powered electric forced hot air hydronic furnace

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011028186A3 (fr) * 2009-09-04 2011-04-28 Marko Matkovic Appareil frigorifique solaire thermique domestique
DE202010001134U1 (de) * 2010-01-20 2010-06-24 Moser, Peter Kombination aus fassadenmontierten Solar-Luft-Kollektor mit integrierter Luft-Wärmepumpe
WO2013176611A1 (fr) 2012-05-21 2013-11-28 Värmestugan Ab Agencement de chauffage permettant de chauffer un fluide grâce à un panneau solaire
CN104620055A (zh) * 2012-05-21 2015-05-13 索勒埃公司 利用太阳能板加热液体的加热装置
JP2015517647A (ja) * 2012-05-21 2015-06-22 ソレトエアー アーベーＳｏｌｅｔａｅｒ Ａｂ 加熱設備
EP2867586A4 (fr) * 2012-05-21 2016-07-20 Soletaer Ab Agencement de chauffage permettant de chauffer un fluide grâce à un panneau solaire

Also Published As

Publication number Publication date
DE112008003356A5 (de) 2010-09-16
WO2009043334A3 (fr) 2009-09-24
EP2198203A2 (fr) 2010-06-23

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