WO2012159763A2 - Installation photovoltaïque et héliothermique combinée - Google Patents

Installation photovoltaïque et héliothermique combinée Download PDF

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Publication number
WO2012159763A2
WO2012159763A2 PCT/EP2012/002228 EP2012002228W WO2012159763A2 WO 2012159763 A2 WO2012159763 A2 WO 2012159763A2 EP 2012002228 W EP2012002228 W EP 2012002228W WO 2012159763 A2 WO2012159763 A2 WO 2012159763A2
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WO
WIPO (PCT)
Prior art keywords
heat
solar module
fluid
heat exchanger
plant
Prior art date
Application number
PCT/EP2012/002228
Other languages
German (de)
English (en)
Other versions
WO2012159763A3 (fr
Inventor
Willi Bihler
Original Assignee
Willi Bihler
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Filing date
Publication date
Application filed by Willi Bihler filed Critical Willi Bihler
Publication of WO2012159763A2 publication Critical patent/WO2012159763A2/fr
Publication of WO2012159763A3 publication Critical patent/WO2012159763A3/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
    • F24D18/00—Small-scale combined heat and power [CHP] generation systems specially adapted for domestic heating, space heating or domestic hot-water supply
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/022—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of two or more media in heat-exchange relationship being helically coiled, the coils having a cylindrical configuration
    • 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
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
    • F24D11/0221—Central heating systems using heat accumulated in storage masses using heat pumps water heating system combined with solar energy
    • 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
    • F24D3/00—Hot-water central heating systems
    • F24D3/08—Hot-water central heating systems in combination with systems for domestic hot-water supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S10/00—Solar heat collectors using working fluids
    • F24S10/70—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits
    • F24S10/74—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits the tubular conduits are not fixed to heat absorbing plates and are not touching each other
    • F24S10/746—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits the tubular conduits are not fixed to heat absorbing plates and are not touching each other the conduits being spirally coiled
    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/14—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically both tubes being bent
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J1/00—Circuit arrangements for dc mains or dc distribution networks
    • H02J1/14—Balancing the load in a network
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J3/00—Circuit arrangements for ac mains or ac distribution networks
    • H02J3/28—Arrangements for balancing of the load in a network by storage of energy
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02S—GENERATION OF ELECTRIC POWER BY CONVERSION OF INFRARED RADIATION, VISIBLE LIGHT OR ULTRAVIOLET LIGHT, e.g. USING PHOTOVOLTAIC [PV] MODULES
    • H02S40/00—Components or accessories in combination with PV modules, not provided for in groups H02S10/00 - H02S30/00
    • H02S40/40—Thermal components
    • H02S40/44—Means to utilise heat energy, e.g. hybrid systems producing warm water and electricity at the same time
    • 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
    • F24D2101/00—Electric generators of small-scale CHP systems
    • F24D2101/40—Photovoltaic [PV] modules
    • 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
    • F24D2103/00—Thermal aspects of small-scale CHP systems
    • F24D2103/10—Small-scale CHP systems characterised by their heat recovery units
    • F24D2103/13—Small-scale CHP systems characterised by their heat recovery units characterised by their heat exchangers
    • 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
    • F24D2103/00—Thermal aspects of small-scale CHP systems
    • F24D2103/10—Small-scale CHP systems characterised by their heat recovery units
    • F24D2103/17—Storage tanks
    • 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
    • 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
    • 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
    • Y02B10/70—Hybrid systems, e.g. uninterruptible or back-up power supplies integrating renewable energies
    • 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
    • Y02E10/50—Photovoltaic [PV] energy
    • Y02E10/56—Power conversion systems, e.g. maximum power point trackers
    • 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
    • Y02E10/60—Thermal-PV hybrids
    • 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
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin

Definitions

  • the present invention is in the field of regenerative energy technology. More specifically, it relates to a combined photovoltaic and solar thermal system. BACKGROUND AND RELATED ART
  • a solar module which comprises photovoltaic solar cells and a solar module heat exchanger.
  • the solar module heat exchanger comprises a fluid line for passing a solar module sulfide and is suitable for transferring heat from the photovoltaic solar cells to the solar module fluid.
  • the heat which the solar module fluid absorbs during the flow through the solar module heat exchangers is used sensibly, for example for hot water heating, etc.
  • this only works really efficiently if the solar module fluid has a higher temperature as the medium to absorb the heat of the solar modulus. This is in the hot water only within limits possible, since at least with less intense sunlight, the temperature of the Solarmodulfiuids this will not be enough.
  • it is possible to increase the penetration of the solar module fluid through slower flow through the solar module heat exchangers. warm, but this will deteriorate the cooling of the solar cells and thus diminished the aspired efficiency gain in the production of electrical power.
  • a larger flow of the solar module fluid through the solar module heat exchanger is preferable, which provides better cooling.
  • the combined photovoltaic and solar thermal system of the invention comprises at least one solar module comprising photovoltaic solar cells and a solar module heat exchanger.
  • the plant will comprise a plurality of solar modules, covering a total of, for example, an area of more than 20 m, preferably even more than 40 m or more than 80 m 2 .
  • the solar module heat exchanger in this case comprises a fluid line for passing a solar module fluid is suitable to transfer heat from the photovoltaic solar cells to the solar module fluid.
  • the plant of the invention comprises a heat storage for storing a heat storage fluid and means for transferring heat from the solar module fluid to the heat storage fluid.
  • the means for transferring heat from the solar module fluid to the heat storage fluid comprises a heat pump having a first heat exchanger for receiving heat from the solar module fluid through a working fluid and a second heat exchanger for delivering heat from the working fluid to the heat storage fluid, the first and second heat exchangers or the second heat exchanger has a double-tube structure which consists of an outer tube or tube and a thermally conductive inner tube or tube arranged therein.
  • the inventor has found that the above-described problems can be solved in a very advantageous and efficient manner in a combined photovoltaic and solar thermal system using such a heat pump.
  • the first heat exchanger of the heat pump has the double tube structure described, very large flow rates of solar module fluid can be passed through the heat pump without the flow resistance increasing excessively.
  • the pumping power required for the solar module fluid is kept comparatively low and thus increases the efficiency of the system as a whole.
  • the ability to accommodate larger flow rates of the solar module fluid has a positive effect in two ways. On the one hand can be achieved by a higher flow rate per solar module more efficient cooling of the solar cell, whereby their efficiency and thus the efficiency of the system is increased as a whole.
  • the number of solar modules in the system can be increased so that even larger roof areas can be used fully and efficiently without significantly increasing the costs for the rest of the system.
  • the heat exchanger with the described double-tube structure can be produced very easily and inexpensively and.
  • the outer tube / the outer tube and / or the inner tube / the inner tube are flexible.
  • the terms “hose” and “pipe” are no longer distinguished, but each type of "hose” is considered a special case of a (flexible) pipe In this way it is possible to arrange even very long double-tube structures rolled up in a housing of moderate dimensions in a simple and space-saving manner and still allow a sufficiently long flow path within the heat exchanger placed a compressor of the heat pump, which may be, for example, a scroll compressor.
  • the outer tube made of synthetic rubber, which is preferably oil resistant and high tensile strength.
  • Such an outer tube is relatively inexpensive, available in virtually any length and can easily roll up to save space.
  • the inner tube is preferably made of copper or stainless steel and is designed in particular as a corrugated tube in order to increase the surface area and thus to increase the efficiency of the heat exchanger.
  • the outer tube has an inner diameter of 15 to 120 mm, preferably from 50 to 100 mm.
  • the inner tube preferably has an inner diameter of 10 to 50 mm, particularly preferably 20 to 40 mm. Such dimensions have proven to be particularly suitable for systems according to the invention.
  • the first heat exchanger has a length of 2 to 30 m, particularly preferably 4 to 15 m.
  • the means for transferring heat from the solar module fluid to the Wärrne Eatfiuid at least one, preferably at least two with respect to the flow of the solar module fluid arranged in parallel third heat exchanger.
  • the heat from the solar panel can be dissipated via this at least one third heat exchanger.
  • module fluid also directly, that are transmitted without detour via the heat pump to the furnished appointedflu- id.
  • This third heat exchanger can be used when the absolute temperature of the solar module fluid and / or the temperature difference between the solar module fluid and the heat storage fluid is sufficiently large to allow efficient direct heat transfer. In this case, the system works particularly efficiently, because the additional energy for the operation of the heat pump can be saved.
  • the heat accumulator comprises a lower portion and an upper portion, wherein in operation the mean temperature in the lower portion of the heat accumulator is lower than in the upper portion.
  • the temperature difference between the average temperature in the lower section and the average temperature in the upper section is preferably at least 15 ° C., particularly preferably at least 30 ° C.
  • the at least one third heat exchanger which is intended for the transfer of heat from the solar module fluid to the heat storage fluid, is preferably arranged in said lower portion of the heat accumulator, d. H. the lower temperature section. In this way, the heat from the solar module fluid can be transferred more efficiently to the heat storage fluid.
  • a means for example, a first changeover valve is provided which is suitable to operatively connect the flow of the solar module optionally with the first heat exchanger associated with the heat pump or the at least one third heat exchanger.
  • the term "operative connection" indicates that the solar module fluid flows either into the heat pump or into the third heat exchanger, but does not presuppose that the respective other fluid connection is physically separated as such Third heat exchanger can also be prevented by the fact that a valve is closed behind the third heat exchanger, for which reason no solar module fluid can flow through the third heat exchanger, even if there is a fluid connection between the solar module and the third heat exchanger This disclosure is intended to understand the term "operative connection”.
  • the first switching valve can optionally be decided, for example, depending on the temperature of the solar module fluid in the flow of the solar module, whether the solar module fluid is used directly for heating the heat storage fluid or in the detour via the heat pump.
  • a hot water heat exchanger is further provided which is suitable for transferring heat from the heat storage fluid to service water.
  • the solar thermal heat ie the heat of the solar module fluid fluctuates with changing solar radiation and is therefore introduced irregularly into the system. typically required at certain peak times (eg in the morning hours), but not at other times, or to a lesser extent.Through the effect of the heat accumulator as an energy buffer, it is possible to mediate between the discontinuous energy supply and discharge.
  • the heat accumulator has a receiving volume for the heat storage fluid of at least 3 m 3 , preferably at least 4.5 m 3 .
  • Such volumes can already be used to generate a very effective energy buffer.
  • the heat storage per kilowatt nominal heat output of the plant has a receiving volume of at least 75 1, preferably of at least 90 1.
  • the heat storage is connected or connected to a heater, which is operable with the heat storage fluid.
  • a fourth heat exchanger is provided between the flow of the at least one solar module and the heat pump, which allows the transfer of heat between a further heat source and the solar module fluid.
  • This further heat source can be formed or fed, for example, by the soil, groundwater or surface water.
  • heat from the further heat source can be transmitted to the solar module fluid via the fourth heat exchanger and then fed into the heat pump together with the solar module fluid.
  • a bypass line is provided, which makes it possible to short-circuit the return of the solar module with its flow, so that a part of the solar module fluid can circulate without flowing through the one or more heat exchangers of the at least one solar module.
  • the bypass line can preferably be opened and closed by actuation of a second changeover valve. This allows a portion of the solar module fluid to circulate through the heat pump and fourth heat exchanger, but without flowing through the solar panels.
  • This mode is particularly advantageous in winter, when the solar module fluid in the flow of the solar module would be colder than the other heat source. In this mode, the solar modules are thermally decoupled, and heat is introduced into the heat pump from the further heat source via the fourth heat exchanger and the circulating part of the solar module fluid, which is separate from the solar modules.
  • a particular advantage of this arrangement is that one and the same heat pump can be used to pump both heat from the solar module and heat from the further heat source in the heat accumulator.
  • the solar module fluid In the process, only the solar module fluid always flows through the heat pump, even if the heat comes effectively from the further heat source and not from the solar modules.
  • the medium of the further heat source for example the groundwater and the solar module fluid are usually different and must not be mixed.
  • the solar module fluid typically contains water and glycol to lower the freezing point, and this mixture should not be mixed with the groundwater.
  • this structure allows a rapid switching between the use of heat from the further heat source and the heat from the solar modules. For example, in the course of a sunny winter day, it is easy to switch between the two operating modes, depending on the temperature which the solar module fluid in the solar modules assumes due to the solar radiation.
  • the further heat source is formed by a delivery well, can be conveyed from the water and passed through the fourth heat exchanger.
  • a means, in particular a third changeover valve is provided, with which the water from the well after passing through the fourth heat exchanger can be selectively returned to the well or to another location, in particular into a sump.
  • the return of the water the fourth heat exchanger in the wells offers itself when the heat demand of the heat accumulator is covered, for example, during a longer sunny period.
  • the water from the well in the fourth heat exchanger can be heated by the warm solar module fluid and returned to the well so that the temperature in the well is gradually increased.
  • the temperature in the well can thus increase by several ° C in the course of a summer, so that the efficiency of the well as heat source is increased in the winter when it is used.
  • the solar module fluid is effectively cooled by the fourth heat exchanger, whereby the solar cells of the solar modules are cooled and increased in their efficiency.
  • the system comprises a controller which, in the event that
  • the predetermined threshold is preferably at least 8 ° C, particularly preferably at least 10 ° C.
  • the controller ensures that in the event that an efficient heating of the heat storage fluid is possible even without the interposition of the heat pump, a direct transfer of heat from the solar module fluid via the at least one third heat exchanger is made to the heat storage fluid, without the heat pump to operate. In this way, the energy for the operation of the compressor of the heat pump can be saved.
  • a suitable criterion for deciding whether the heat of the solar module fluid is transferred directly via the third heat exchanger or the heat pump to the heat storage fluid is a temperature difference between the temperature of the solar module fluid in the flow of the solar module and the heat accumulator in the area in which the third heat exchanger actually arranged.
  • the corresponding threshold can be adjusted to maximize energy efficiency, but in the preferred embodiment is at least 8 ° C, more preferably at least 10 ° C.
  • the plant comprises a controller which, in the event that
  • the temperature of the solar module fluid in the flow of the at least one solar module falls below a predetermined threshold value
  • the controller ensures that the solar module fluid is fed into the heat pump at too low a temperature, thereby more efficiently heating the heat storage fluid.
  • the system comprises a controller which, in the event that the heat accumulator has no need for heat absorption, causes, in particular by actuation of the first changeover valve, that the flow of the at least one solar module is connected to the first heat exchanger associated with the heat pump , the compressor of the heat pump is not put into operation, and water from the well is passed through the fourth heat exchanger and back into the well.
  • the controller ensures that the water from the well is heated by the sodium sulfide and at the same time the solar module is cooled by the water of the well to increase the efficiency of the solar cells.
  • This mode will mainly be used in prolonged sunny and warm periods, and will effectively allow the storage of excessively available thermal energy. energy in the pumping well, which can sometimes be recovered through the heat pump at cold seasons.
  • the system comprises a controller which, in the event that the temperature of the solar module fluid in the flow of the at least one solar module is lower than the temperature of the water in the well, causes the bypass line to open between the return of the solar module and its supply to permit circulation of a portion of the solar module fluid without passing through the heat exchanger (s) of the at least one solar module, and causing water to be directed from the well through the fourth heat exchanger.
  • the controller effectively exchanges the solar modules as a heat source against the well as a heat source, but still passes the solar module fluid through the heat pump. In this way, it is easy and flexible to change between the heat sources depending on the current climatic conditions.
  • the controller is further configured to ablate or at least melt snow on the at least one solar module.
  • the controller causes the solar module fluid, which is colder than the temperature in the heat accumulator, to be passed through the third heat exchanger. In this way, the solar module fluid is warmed up by the heat accumulator. Although heat is withdrawn from the heat storage, this is energetically meaningful if the solar cells are thereby freed of snow and can be used to generate electricity.
  • the snow typically also does not have to be melted off, but only thawed to the extent that a film of water forms between the solar module and the snow cover, on which the snow can then slide down from the solar module.
  • the solar module fluid which is colder than the water in the well, is passed simultaneously with the water from the well through the fourth heat exchanger.
  • the snow is effectively drained or thawed by heat from the well. This is the more energy efficient way, which is preferable if a well is present.
  • Fig. 2 is a sectional view of a solar module for use in the system of Fig. 1 and
  • FIG. 3 is a schematic plan view of a heat pump for use in the system according to FIG. 1.
  • FIG. 1 shows a schematic view of a combined photovoltaic and solar thermal system according to an embodiment of the invention.
  • the system 10 comprises 72 combined photovoltaic and solar thermal modules, which will be referred to below as “solar module” 12.
  • solar module 12 are known per se from the prior art and are sold under the product name "PV-Therm” by the patent applicant.
  • 2 shows a schematic sectional drawing of a solar module 12.
  • the solar module 12 is constructed on its upper side like a conventional photovoltaic module.
  • the interconnected by solder strips (not shown) polycrystalline solar cells 14 are embedded below and above in a transparent plastic layer of ethylene vinyl acetate (EVA) 16. This layer provides for a firm connection of the cells 14 between see a glass sheet 18 and a Tedlarfolie 20th
  • a galvanized and painted steel tub 22 On the underside of the solar module 12 is a galvanized and painted steel tub 22, in which a plurality of channels 24 are formed, which are traversed by a solar module fluid 26.
  • the steel tub 22 therefore serves as a heat exchanger, which is suitable for transferring heat from the solar cells 14 to the solar module fluid 26.
  • the solar module fluid 26 is conducted via a feed A of the solar modules 12 from the solar modules 12 to a first switching valve 28.
  • the solar module fluid is passed through a third heat exchanger 30, which is arranged in a heat storage 32.
  • a plurality of third heat exchangers 30 arranged in parallel can also be provided, between which the flow of the solar module fluid 26 is split.
  • the solar module fluid 26 is passed, after passing through the third heat exchanger 30 along a path C, by a pump 32 to a second switching valve 34.
  • the solar module fluid can either enter the return D of the solar modules 12 or in a bypass line 36, which allows the return of the solar modules 12 short-circuited with their flow A, so that a part of the solar module fluid 26 can circulate through the Solar modules 12 to flow.
  • the solar module fluid at the first switching valve 28 can be conducted into branch E, along which it is passed through a fourth heat exchanger 38 into a first heat exchanger 40 of a heat pump 42.
  • the solar module fluid 26 is passed after passage through the first heat exchanger 40 of the heat pump 42 along a path F, which coincides with the path C and via the pump 32, the second switching valve 34 leads to the return D of the solar modules 12.
  • the switching valve could be arranged with the same effect at the meeting point of the paths C and F.
  • the heat pump 42 shown only schematically in FIG. 1 contains, in addition to the first heat exchanger 40, a second heat exchanger 44 and a working medium circuit 46 which mediates between the first and the second heat exchangers 40, 44.
  • a pump 48 By means of a pump 48, a heat storage fluid from the heat accumulator 32 is pumped through the second heat exchanger 44, heated therein and returned to the heat accumulator 32.
  • a hot water heat exchanger 50 is arranged in the heat accumulator 32.
  • Cold water can be pumped by a pump 52 through the hot water heat exchanger 50, thereby heated and fed to a hot water circuit 54.
  • the hot water cycle will generally not be a cycle in the true sense, as the used water is not returned, but supplemented by fresh cold water.
  • the heat accumulator 32 is from top to bottom, a temperature gradient. Roughly speaking, the heat accumulator 32 may be placed in an upper portion 32a having a higher mean temperature and a lower portion 32b having a lower mean temperature divide.
  • the temperature difference between the average temperature in the upper section 32a and in the lower section 32b is typically at least 15 ° C, preferably at least 30 ° C during operation.
  • the third heat exchanger 30 is disposed in the lower, ie colder, portion 32b of the heat accumulator 32, whereby the heat transfer between the solar module fluid 26 and the heat storage fluid in the heat accumulator 32 is more efficient.
  • a heating circuit 56 for example, for a floor heating (not shown) fed.
  • the flow of the heat storage fluid through the heating circuit 56 is driven by a pump 58.
  • a groundwater delivery well 60 is provided from which groundwater can be pumped along a path G through the fourth heat exchanger 38 by means of a feed pump 62. Downstream of the fourth heat exchanger 38, the groundwater is guided along a path H to a third switching valve 64. By actuating the third switching valve 64, the groundwater can either be directed back into the wells 60 or into a sump well 66.
  • an inverter device 68 is provided, via which the solar power from the solar modules 12 can be fed into the network. Furthermore, the inverter device 68 supplies the heat pump 42 with electricity via an electrical line 70. Finally, with the solar power and a battery can be charged.
  • the invention therefore provides a special heat pump 42 which is shown in more detail in FIG.
  • the first heat exchanger 40 consists of a double tube structure with an outer tube 72 and an inner tube 74. Through the outer tube 72, the solar module fluid 26 flows, namely from the line section E into the heat pump 42 and out of the heat pump 42 in the Section F (see Fig. 1).
  • the working medium of the heat pump flows, in the opposite direction as the solar module fluid.
  • the outer tube 72 is made of an oil resistant, high tensile synthetic rubber
  • the inner tube 74 is a corrugated tube of copper or stainless steel.
  • the second heat exchanger 44 is basically constructed similarly.
  • the heat storage fluid flows from the heat accumulator 32 (see Fig. 1) through the outer tube 72 of the second heat exchanger 44 and back into the heat accumulator 32, while the working fluid flows in the inner tube 74 in the opposite direction.
  • the inner tubes 74 in the first and second heat exchangers 40, 44 together with an expansion valve 76 and a scroll compressor 78 form the working medium circuit 46 of the heat pump 42.
  • both heat exchangers 40, 44 are space-saving in loops placed the scroll compressor 78.
  • the whole assembly can be arranged in a housing 80 of moderate size, even with a length of the first heat exchanger 40 of for example 25 m.
  • the warm solar module fluid flows in countercurrent to the working medium and releases heat to the working medium.
  • the working medium is compressed by the scroll compressor 78, whereby the temperature increases.
  • This now relatively hot working fluid is introduced at position ⁇ in the second heat exchanger 44 and flows in countercurrent to the heat storage fluid of the heat accumulator 32 to heat it.
  • the inner tube 74 exits the outer tube 72 and the working fluid is led to the expansion valve 76 and expanded therein between the ® and ® positions and thereby further cooled, returning the circuit to its starting point CD.
  • the construction of the heat pump 42 of FIG. 3 has the particular advantage that it can cope with very high flow rates of the solar fluid medium without generating an excessively large flow resistance. This also succeeds with a surprisingly low design effort.
  • a flow rate of, for example, 3,600 l per hour one would have to use a multiplicity of heat exchangers usually used in heat pumps. Arranging rallel, which would be unfavorable and also hydraulically difficult to accomplish both in terms of manufacturing costs and the space required.
  • the diameter and length of the first and second heat exchangers 40, 44 depends on the expected amount of solar module fluid. Suitable lengths for the first heat exchanger 40 are between 2 and 30 m.
  • the inner diameter of the outer tube 72 is preferably 15 to 120 mm, particularly preferably 50 to 100 mm.
  • the inner diameter of the inner tube 74 is adapted to the inner diameter of the outer tube 72 and is typically between 10 and 50 mm, preferably 20 to 40 mm.
  • the system 10 further includes a controller (not shown) which controls a plurality or all of said pumps and valves to control operation of the system as a whole.
  • This controller is further connected to a plurality of temperature sensors (not shown) and adapted to set the optimum operating mode based on temperature measurements.
  • Scenario I the case is considered that the temperature of the solar module fluid 26 in the lead A of the solar modules 12, hereinafter referred to as T_PVT, is 30 ° C or warmer, and that TJPVT the temperature in the lower portion 32b of the heat accumulator by at least 10 % exceeds.
  • the controller determines that the heat storage 32 still has a need for heat absorption.
  • the solar module fluid may be used directly for heating the heat storage fluid through the third heat exchanger 30. Accordingly, the first switching valve 28 is switched so that the solar module fluid along the path A - B -> C - D is passed.
  • the heat pump 42 is not needed in this case.
  • the heat from the solar module fluid can be used to heat the groundwater in the well 60.
  • the first switching valve 28 is switched so that the solar module Dulfluid 26 is passed through the fourth heat exchanger 38 and the heat pump 42, which is not in operation, ie, the solar module fluid 26 is guided along the paths A -> E -> F -> D.
  • the solar module fluid 26 is passed through the first heat exchanger 40 of the heat pump 42, but in which there is no heat exchange, because the heat pump 42 is not in operation. It proves to be very advantageous that the first heat exchanger 40 of the heat pump 42 has a relatively low flow resistance due to its double tube structure.
  • groundwater from the well 60 is directed back into the well 60 via the pump 62 along the path G through the fourth heat exchanger 38, along the path H, and through the third switching valve 64.
  • heat is transferred from the solar module fluid 26 to the groundwater, d. H. the solar module fluid 26 is cooled and the groundwater is heated.
  • Scenario III relates to the case where heat storage 32 does request heat, but T PVT is too low to heat heat storage fluid directly via third heat exchanger 30 in an efficient manner. This case, for example, occurs in the summer in bad weather.
  • the heat pump 42 is used.
  • the first switching valve 28 is switched so that the solar module fluid 26 is guided along the paths A and E in the first heat exchanger 40 of the heat pump 42 and is pumped via the paths F and D back to the solar modules 12.
  • the heat pump 42 is put into operation and pumps heat from the solar module fluid 26 via the working medium circuit 46 and the second heat exchanger 44 in the heat storage fluid.
  • Scenario III is basically used as long as the heat store 32 has a heat requirement and T_PVT is above the temperature of the water in the delivery well 60.
  • Scenario V relates to the defrosting of snow on the solar modules 12.
  • Snow on solar modules is a major problem, as photovoltaic systems have comparatively high efficiency in winter due to the low outside temperature and are therefore able to generate high electricity yields.
  • the snow prevents the sunlight from penetrating to the modules 12.
  • the solar modules 12 In order to use the hours of sunshine even in snowy winters, therefore, the solar modules 12 would have to be cleared of the snow by hand, which is tedious and dangerous because of the danger of falling.
  • the snow-covered solar modules 12 are temporarily heated by the solar module fluid 26 in order to at least apply the snow as far as possible. Thaw that forms between the snow and the solar module 12, a water film on which the snow then slides down by its own weight.
  • the solar modules 12 are basically two variants.
  • the more advantageous variant is to use the heat from the delivery well 60 for this purpose.
  • the solar module fluid would pass through the circuit A -> E -> F -> D, and the water from the well 60 along the path G in the fourth heat exchanger 38 and along the path H and the third switching valve 64 in the Swallow well 66 run.
  • the snow on the solar module 12 would be effectively melted with heat from the well 60.
  • the features shown and described may be of importance in any combination.
  • the shown system 10 can be scaled well in size.
  • the inventor has determined that optimally about 2.4 m solar thermically active solar module surface should be present per kilowatt of desired heating power. This corresponds to about two solar modules of the type PV-Therm per kilowatt heating power. Preferably, however, at least 0.75 m, particularly preferably 1 m, of active solar module area are provided per kilowatt of heating power.
  • the system should be capable of conducting at least 25 l per hour, preferably at least 32 l per hour and more preferably at least 38 l per hour of solar module fluid through the heat pump 42 per square meter of solar module area. This is virtually impossible to achieve with systems with large solar module areas of 50 m, 100 m or more with conventional heat pumps.
  • the structure of the heat pump 42 shown in FIG. 3 this can be realized in a simple, space-saving and cost-effective manner.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Power Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Water Supply & Treatment (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Photovoltaic Devices (AREA)

Abstract

L'invention concerne une installation photovoltaïque et héliothermique combinée (10) comprenant au moins un module solaire (12) comprenant des cellules solaires photovoltaïques (14) et un échangeur de chaleur de module solaire (22). L'échangeur de chaleur de module solaire (22) comprend une conduite de fluide (24) permettant le passage d'un fluide de module solaire (26) et est adapté pour transférer de la chaleur des cellules solaires photovoltaïques (14) au fluide de module solaire (26). Ladite installation photovoltaïque et héliothermique comprend également un accumulateur de chaleur (32) destiné à stocker un fluide accumulateur de chaleur et des moyens (30, 42) destinés à transférer la chaleur du fluide de module solaire (26) au fluide accumulateur de chaleur, les moyens de transfert de chaleur du fluide de module solaire (26) au fluide accumulateur de chaleur comprenant une pompe à chaleur (42) munie d'un premier échangeur de chaleur (40) destiné à absorber de la chaleur du fluide de module solaire (26) à l'aide d'un fluide de travail et d'un deuxième échangeur de chaleur (44) destiné à fournir de la chaleur du fluide de travail au fluide accumulateur de chaleur. Le premier et/ou le deuxième échangeur de chaleur (40, 44) présentent une structure à deux tubes constituée d'un tube ou tuyau extérieur (72) et d'un tube ou tuyau intérieur (74) thermoconducteur agencé à l'intérieur.
PCT/EP2012/002228 2011-05-26 2012-05-24 Installation photovoltaïque et héliothermique combinée WO2012159763A2 (fr)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014160929A1 (fr) * 2013-03-29 2014-10-02 SunEdison Energy India Private Limited Procédés et systèmes pour régulation de température de dispositifs et traitement d'énergie thermique obtenue par ceux-ci
US20180066438A1 (en) * 2016-09-06 2018-03-08 Ryan White Solar Powered Heated Roof
CN117894867A (zh) * 2024-03-14 2024-04-16 四川蜀旺新能源股份有限公司 一种光伏热电联供用真空层玻璃组件

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202013008494U1 (de) 2013-09-24 2013-11-21 Institut für Solarenegerieforschung GmbH Solarheizung mit photovolatisch-thermischen Kollektor
ITPV20130011A1 (it) * 2013-12-30 2015-07-01 Antonio Covello Gruppo fornitore integrato di energia termica e di acqua a temperatura controllata
DE102014212481A1 (de) * 2014-06-27 2015-12-31 Witzenmann Gmbh Wellrohr für eine Trinkwasserinstallation
NL2024043B1 (en) * 2019-10-18 2021-06-22 Viridi Holding B V Energy system and method, and data carrier comprising instructions therefor
CN116182432B (zh) * 2023-02-22 2024-04-19 大连理工大学 交替除霜不间断供热的复叠式压缩pvt-空气源热泵系统

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007144113A1 (fr) 2006-06-13 2007-12-21 Willi Bihler Élément solaire avec dispositif de régulation de température

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2931606A1 (de) * 1979-08-03 1981-02-19 Prechtl Heizung & Lueftung Waermepumpensystem
DE3027070A1 (de) * 1980-07-17 1982-02-18 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München Koaxialwaermetauscher
DE10300427B4 (de) * 2003-01-09 2007-09-13 Consolar Solare Energiesysteme Gmbh Solarsystem mit Wärmepumpe
DE202008008747U1 (de) * 2008-07-02 2008-11-27 Giritsch, Johann Photovoltaikanlage
DE102008059544A1 (de) * 2008-11-30 2010-06-02 Solarhybrid Ag Brauchwassererwärmer, Brauchwasserversorgungssystem mit einem Brauchwassererwärmer sowie Verfahren zu deren Betrieb
ITMI20090563A1 (it) * 2009-04-08 2010-10-09 Donato Alfonso Di Riscaldamento e/o condizionamento e/o trattamento aria con sostanze fotocatalitiche utilizzando impianti fotovoltaici a concentrazione con raffreddamento con pompa di calore e/o essicamento dell'aria
JP5205353B2 (ja) * 2009-09-24 2013-06-05 株式会社日立製作所 ヒートポンプ発電システム

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007144113A1 (fr) 2006-06-13 2007-12-21 Willi Bihler Élément solaire avec dispositif de régulation de température

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014160929A1 (fr) * 2013-03-29 2014-10-02 SunEdison Energy India Private Limited Procédés et systèmes pour régulation de température de dispositifs et traitement d'énergie thermique obtenue par ceux-ci
US20180066438A1 (en) * 2016-09-06 2018-03-08 Ryan White Solar Powered Heated Roof
WO2018048386A1 (fr) * 2016-09-06 2018-03-15 Ryan White Toit chauffé alimenté par énergie solaire
CN117894867A (zh) * 2024-03-14 2024-04-16 四川蜀旺新能源股份有限公司 一种光伏热电联供用真空层玻璃组件

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WO2012159763A3 (fr) 2013-05-10

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