EP2388540A1 - Unite de pompe a chaleur de type a accumulation froid / chaud a entrainement hybride utilisant une alimentation photovoltaique solaire et une alimentation commerciale - Google Patents

Unite de pompe a chaleur de type a accumulation froid / chaud a entrainement hybride utilisant une alimentation photovoltaique solaire et une alimentation commerciale Download PDF

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Publication number
EP2388540A1
EP2388540A1 EP10731055A EP10731055A EP2388540A1 EP 2388540 A1 EP2388540 A1 EP 2388540A1 EP 10731055 A EP10731055 A EP 10731055A EP 10731055 A EP10731055 A EP 10731055A EP 2388540 A1 EP2388540 A1 EP 2388540A1
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EP
European Patent Office
Prior art keywords
heat
cold
sub
heat storage
refrigerant
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Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP10731055A
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German (de)
English (en)
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EP2388540A4 (fr
Inventor
Weixing Yuan
Yufei Yang
Xiugan Yuan
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Beihang University
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Beihang University
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Filing date
Publication date
Application filed by Beihang University filed Critical Beihang University
Publication of EP2388540A1 publication Critical patent/EP2388540A1/fr
Publication of EP2388540A4 publication Critical patent/EP2388540A4/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/2111—Temperatures of a heat storage receiver

Definitions

  • the present invention relates to a heat pump system, and more particularly relates to a dual-power-source heat pump system with hybrid driving by a solar energy photovoltaic DC power and an ordinary commercial power.
  • a heat pump type water heater has an coefficient of performance (COP) greater than 1, it can generate 3-4 kW heat for water by only 1 kW of electrical power it consumes, so it has a more remarkable energy-saving effect as compared with an ordinary electrical water heater.
  • COP coefficient of performance
  • a cold and hot water system with heat pump water cooling type refrigerator
  • water cooling type refrigerator can produce cold water by producing hot water, and the hot water it produces can be used for domestic water or for heating, while the cold water can be used for air conditioning, so it is expected to be a core device of a future family central energy system and will be of significance to improvement of people's life quality.
  • a typical solar water heater is a device that collects energy of sunlight using plate heat collector, vacuum tube heat collector, or etc. to heat cool water. It can not produce cold water while producing hot water. Moreover, although solar energy is clean energy of endless supply it is intermittent and whether-dependent and can only be effective during sunny daytime, it is not applicable in cloudy day or at night, when hot water is mostly needed.
  • the common existing solar photovoltaic power driven vapor compression refrigeration system makes use of DC-to-AC inverter, that is, it raises voltage of the DC provided by a solar cell panel in the first place, then converts the DC into AC, and then drives an AC compressor with the AC power; however, an inverter is expensive and sophisticated, resulting in increase of the cost of the system.
  • An aim of the present invention is to provide a solar photovoltaic-commercial electricity dually driven heat pump system with cold/heat storage, which can be dually driven by a solar photovoltaic power source and ordinary commercial power source.
  • the solar photovoltaic-commercial electricity dually driven heat pump system with cold/heat storage comprises: a compressor module, which includes a DC compressor sub-system; a photovoltaic DC power source sub-system, which is coupled to said DC compressor sub-system; an air source condenser; a throttle device; an air source evaporator; a heat storage sub-system coupled between said compressor module and said condenser and containing heat storage phase change material for absorbing heat from refrigerant; a cold storage sub-system coupled between said throttle device and said evaporator and including cold storage phase change material to be refrigerated by said refrigerant; said compressor module, said heat storage sub-system, said condenser, said throttle device, said cold storage sub-system, and said evaporator form into a loop by pipes, with refrigerant circulating within said loop.
  • said compressor module further comprises an AC compressor sub-system connected in parallel with said DC compressor sub-system.
  • four solenoid valves are provided in said compressor module for controlling the states of the AC compressor of said AC compressor sub-system and the DC compressor of said DC compressor sub-system connected in the refrigerant circulating loop.
  • said heat storage sub-system comprises a heat storage container having good thermal insulation and containing heat storage phase change material therein; said cold storage sub-system comprises a cold starage container having good thermal insulation and containing cold storage phase change material therein.
  • Said heat storage sub-system can further comprises: a first coil heat exchanger arranged inside said heat storage container and connected in said refrigerant circulating loop, for allowing heat exchange between refrigerant in it and said heat storage phase change material.
  • those arranged in the refrigerant circulating loop include: a first solenoid valve, for bypassing the refrigerant so the refrigerant does not go through the air source condenser; a second solenoid valve, for bypassing the refrigerant so the refrigerant does not go through the air source evaporator; a third solenoid valve, for bypassing the refrigerant so the refrigerant does not go through the heat storage sub-system; and, a forth solenoid valve, for bypassing the refrigerant so the refrigerant does not go through the cold storage sub-system.
  • a first temperature sensor is provided in the heat storage sub-system for detecting the temperature of the heat storage phase change material in order to determine whether to open or close the first and the third solenoid valve; and, a second temperature sensor is provided in the cold storage sub-system for detecting the temperature of the cold storage phase change material in order to determine whether to open or close the second and the forth solenoid valve.
  • the heat storage phase change material can be one selected from paraffin, hydrated salt, and sodium sulfate decahydrate, while the cold storage phase change material can be one selected from glycerol, water, hydrated salt, and paraffin.
  • the photovoltaic DC power source sub-system comprises a solar cell assembly, a junction box, a storage battery, and a power and voltage regulator.
  • a high pressure sensor is provided in the high pressure pipe line of the heat pump system, a low pressure sensor is provided in the low pressure pipe line, and a safety valve is provided in the heat storage sub-system and the cold storage sub-system respectively.
  • the solar photovoltaic-commercial electricity dually driven heat pump system with cold/heat storage has dual compressors, a DC compressor and an AC compressor, which are complementary to each other.
  • the DC refrigeration compressor is driven directly by DC current generated by solar cell panel to produce cold and heat, the produced cold and heat can be stored by phase changed material (PCM) respectively so as to remedy the disadvantage that solar energy is intermittent and whether dependent.
  • PCM phase changed material
  • two refrigeration compressors are provided in the present invention: a DC compressor and an AC compressor; when solar energy is adequate, the AC compressor does not operate; when both the solar energy and the stored energy are inadequate, the AC compressor is connected to commercial power grid for replacing the DC compressor.
  • the phase change energy storage device provided in the present invention stores hot water and cold water produced by heat pump, so an allocation can be made between the time intervals of collecting solar energy and those of consuming solar energy, and an allocation can be made between the high production rate of cold/hot water and low amount of consumption by the users, to allow efficient utilization of solar energy and avoid unnecessary waste.
  • solar energy and heat pump water heater systems are combined so cold water is produced at the same time hot water is produced.
  • solar photovoltaic cell panel is used to generate DC power, whose voltage is then raised and power regulated to drive a vapor compression refrigerator unit; hot water is produced at the condenser side of the refrigerator, while cold water is produced at the evaporator side of the refrigerator.
  • the system of the present invention Comparing with existing solar photovoltaic vapor compression refrigerator system, the system of the present invention needs no DC-AC converter while the area of solar cell panel can be greatly reduced due to a shared load mechanism of power.
  • the system of the present invention overcomes the limit of solar energy while it makes a full use of solar energy, and it has remarkable cost advantage.
  • the main body of the solar photovoltaic-commercial electricity dually driven heat pump system with cold/heat storage is a heat pump system; cold water can be produced at the evaporator side of the heat pump system while hot water can be produced at the condenser side of it. Cold and heat energy is stored by phase change materials respectively to eliminate the conflict of the difference between operation time interval of the heat pump system and the usage time interval of cold/hot water.
  • the core part of the heat pump system includes two complementary compressors, a DC compressor and an AC compressor.
  • the DC compressor operates with the DC power generated by the solar photovoltaic system, while the AC compressor operates with the commercial AC power.
  • an embodiment according to the present invention comprises a DC compressor sub-system A, an optional AC compressor sub-system B, a heat storage sub-system C, a air source condensor D, a fluid storage device E, a dryer filter F, an expansion valve or throttle device G, a cold storage sub-system H, a fin evaporator I, and a photovoltaic DC power source sub-system K.
  • the connection relationships in such an embodiment is that sub-systems A and B are connected in parallel, and that the parallel-connected sub-systems A and B are connected by pipe lines with sub-systems C, D, E, F, G, H, and I to form a closed loop, in which refrigerant circulates.
  • An AC power supply sub-system J is connected by wire to a junction box of AC compressor sub-system B.
  • the photovoltaic DC power source sub-system K is connected by wire to a junction box of DC compressor sub-system A.
  • DC compressor sub-system A comprises a DC compressor 2, a solenoid valve 1 arranged on the exhaust pipe of DC compressor 2, an solenoid valve 3 arranged on the air intake pipe of DC compressor 2.
  • AC compressor sub-system B comprises an AC comprissor 8, a solenoid valve 7 and a tee joint 6 arranged on the exhaust pipe of AC compressor 8, a solenoid valve 9 and a tee joint 10 arranged on the air intake pipe of AC compressor 8.
  • Heat storage sub-system C comprises a container (heat storage tub) 17 having good thermal insulation, a safty valve 18, a temperature sensor 19, phaseheat storage phase change material 20 contained in the heat storage tub 17, a hot water outlet valve 21, a hot water return valve 22, a coil heat exchanger 23, a refrigerant outlet valve 24, a refrigerant inlet valve 25, a coil heat exchanger 26, a tee joint 27, a bypass solenoid valve 28, and a tee joint 29.
  • the temperature sensor 19 is provided at the top of the heat storage tub 17.
  • Bypass solenoid valve 28 is provided on the inlet and outlet pipes of the heat storage sub-system and is normally closed.
  • Air source Condenser D comprises a blower 33, a fin-tube heat exchanger 34, a tee joint 30, a solenoid valve 31, and a tee joint 32.
  • Cold storage sub-system H comprises a container (cold storage tub) 38 having good thermal insulation for containing cold storage phase change material 39, a refrigerant outlet valve 40, a refrigerant inlet valve 41, a temperature sensor 42, a coil heat exchanger 43, a cold water return valve 44, a cold water outlet valve 45, a coil heat exchanger 46, a safety valve 47, a tee joint 35, a bypass solenoid valve 36, and a tee joint 37.
  • Temperature sensor 42 is arranged at the lower end of cold storage tub 38.
  • Bypass solenoid valve 36 is provided at the inlet and outlet pipes of the cold storage sub-system and is normally closed.
  • Air source evaporator I comprises a blower 52, a fin-tube heat exchanger 51, a tee joint 48, a solenoid valve 49, and a tee joint 50.
  • AC power supply sub-system J comprises an AC junction box 55 and wire 54 connecting to AC compressor 8.
  • Photovoltaic DC power supply sub-system K comprises a solar cell assembly 60, a junction box 59, a storage battery 58, a power and voltage regulator 57, and wire 56 connecting to DC refrigeration compressor 2. These parts are connected by wires as shown in Fig. 1 . Photovoltaic DC power supply sub-system K is for receiving sunlight to generate DC power supply for operation of DC refrigeration compressor 2.
  • heat storage phase change material 20 in heat storage tub 17 is in solid state, while cold storage phase change material 39 in cold storage tub 38 is in liquid state.
  • a thermal characteristic of heat storage phase change material 20 is: while it is in solid state at an initial temperature, when it is heated to its melting point, it begins partly melting and stays in a solid-liquid mixture state, and its temperature keeps substantially unchanged in this state, until it is wholly changed into liquid. Only then will its temperature raise further if it is heated further.
  • Heat storage phase change material 20 can be paraffin, hydrated salt, and sodium sulfate decahydrate" or so on, which has such characteristic.
  • a thermal characteristic of cold storage phase change material 39 is: while it is in liquid state at an initial temperature, when it is cooled to release heat and its temperature is lowered to its freezing point, it begins to partly solidified and stays in a solid-liquid mixture state while its temperature keeps substantially unchanged in this state, until it is wholly changed into solid state. Only then will its temperature drop further if it is cooled further, cold storage phase change material 39 can be glycerol, paraffin, hydrated salt or the like.
  • a heat pump system of the present invention is supplied with power by solar photovoltaic DC power supply sub-system.
  • the solar cell panel comprises a plurality of solar cell assembly 60 connected in series and in parallel in a predetermined manner to meet preset voltage and current requirements.
  • the photovoltaic power supply is connected to junction box 59, and supply power to DC compressor 2 after power regulation and voltage stabilization by power and voltage regulator 57. When DC compressor 2 is not on duty, surplus electrical energy can be stored in storage battery 58.
  • DC compressor 2 is driven by DC power supply.
  • the direction of the refrigerant circulation is: refrigerant in the system sequentially goes through A ⁇ C ⁇ D ⁇ E ⁇ F ⁇ G ⁇ H ⁇ I ⁇ A.
  • solenoid valves 1 and 3 are in their opened state under control of the system controller
  • solenoid valves 7 and 9 are in their closed state under control of the system controller
  • wire 56 is in connected state
  • wire 54 is in disconnected state.
  • AC compressor 8 and DC compressor 2 do not work at the same time.
  • Refrigerant vapor is compressed by DC compressor 2 into high-temperature and high-pressure vapor, then it heats heat stroage phase change material 20 through coil heat exchanger 23. With its rise in temperature, heat stroage phase change material 20 undergoes phase change from solid to liquid, while the refrigerant vapor is partially cooled. After heat stroage phase change material 20 is heated, it can functions as a heat source for transmitting heat to coil heat exchanger 26 to supply hot water to outside.
  • the partially cooled refrigerant vapor then enters air source heat exchanger 34 to be cooled further; its heat of condensation is carried away by airflow by condenser blower 33 and is dissipated into the atmosphere. At the outlet of condensor D, all of the refrigerant vapor is converted into liquid.
  • fluid storage device E functions to adjust the circulation amount of refrigerant in the system against variation due to cold/heat load so as to ensure that the pressure flunctuation in the system is not too great.
  • Dryer filter F functions to filtrate impurity in the circulating refrigerant to keep the system clean and to absorb water in the refrigerant to prevent it from freezing to clog the throttle device.
  • the expansion valve or throttle device G can be a capillary, a thermostatic expansion valve, an electronic expansion valve, or an orifice control valve.
  • the refrigerant liquid is throttled by the throttle device G, its pressure is lowered, and it partly transforms into flash vapor and its temperature is also lowered, and it changes into a vapor-liquid mixture.
  • the vapor-liquid mixture of refrigerant enters into coil heat exchanger 46 in cold storage tub 38 and air source evaporator I in sequence and absorbs heat. At the outlet of the air source evaporator I, the refrigerant is completely transformed to vapor, which then enters into DC compressor 2 to begin the next cycle.
  • Cold storage phase change material 39 in cold storage tub 38 is frozen so that phase change from liquid to solid happens. After cold storage phase change material 39 is frozen, it can be used as a cold source for transmitting cold to coil heat exchanger 43 and to supply cold water to outside.
  • AC compressor 8 is ordinarily a backup.
  • DC compressor 2 cannot work due to insufficient DC power supplied by solar sub-system K
  • AC compressor operates to replace DC compressor 2.
  • the power supply of AC compressor 8 is from AC junction box 55, while the current of AC junction box 55 is from commercial electricity grid.
  • the flow of refrigerant is: refrigerant in the system flows sequentially B ⁇ C ⁇ D ⁇ E ⁇ F ⁇ G ⁇ H ⁇ I ⁇ B.
  • solenoid valves 7 and 9 are opened under the control of system controller, solenoid valves 1 and 3 are closed under the control of system controller, wire 54 is connected, and wire 56 is disconnected.
  • Both heat storage sub-system C and air source condenser D supply heat to the outside and carry the heat load of the heat pump system, so these two sub-system can work either at the same time or not.
  • solenoid valve 31 When solenoid valve 31 is opened under the control of a controller, refrigerant is bypassed to move directly from tee joint 30 to tee joint 32 without passing the fin-tube heat exchanger 34 (since its pipe is relatively long, resistance is great correspondingly; if the resistances in the two pathways do not differ very much, an additional solenoid valve can be provided at the inlet of the fin-tube heat exchanger 34 to completely cut-off this pathway;) at this time, air source condensor D does not work and it is not necessary for blower 33 to operate.
  • the time at which air source condensor D begins to operate can be determined by the temperature of heat storage phase change material 20. For example, according to a preferred operation mode, assuming that solid-liquid transition temperature of the phase transition heat storage phase change material is Th, the temperature detected by temperature sensor 19 is T1, then:
  • the temperature of heat storage phase change material 20 can be controlled to be kept always within a predetermined temperature range, that is, it is ensured that the high pressure the heat pump system is not too high and is always kept in a predetermined range.
  • solenoid valve 28 can work and refrigerant vapor is bypassed. Release of heat by condensation of refrigerant is carried out completely by air source condenser D.
  • both cold storage sub-system H and air source evaporator I in the heat pump system absorb heat from outside and carry the cold load of the heat pump system; thus, the two sub-systems may work either simultaneously or at different times.
  • solenoid valve 49 is at work under the control of a controller, refrigerant is bypassed and arrives at tee joint 48 from tee joint 50 without passing the tube of fin-tube heat exchanger 51 (an solenoid valve can also be provided at the inlet of the fin-tube heat exchanger 51 to completely cut-off this pathway;) at this time, air source evaporator I does not operate, and it is not necessary for blower 52 to operate.
  • the time at which air source evaporator I begins to operate can be determined by the temperature of cold storage phase change material 39. For example, according to a preferred operation mode, assuming that liquid-solid transition temperature of the phase cold storage phase change material is Tc, the temperature detected by temperature sensor 42 is T2, then:
  • the temperature of cold storage phase change material 39 can be controlled to be always within a predetermined temperature range, that is, it is ensured that the low pressure of the heat pump system is not too low and is always kept within a predetermined range.
  • solenoid valve 36 can work and refrigerant is bypassed. Absorption of heat is carried out completely by air source evaporator I.
  • a high pressure sensor 4 is provided in the high pressure pipe line of the system and a low pressure sensor 5 is provided in the low pressure pipe line of the system, when an over-high presure or an over-low pressure is detected, operation of all compressors and blowers is stopped to ensure safety of the system.
  • safety valves 18 and 47 are provided on heat storage tub 17 and cold storage tub 38 respectively.
  • the safety valves open automatically to release part of the material so as to lower the pressure within the container, thereby further inhancing the safety of the system.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP10731055.9A 2009-01-15 2010-01-15 Unite de pompe a chaleur de type a accumulation froid / chaud a entrainement hybride utilisant une alimentation photovoltaique solaire et une alimentation commerciale Withdrawn EP2388540A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200910076400.XA CN101458005B (zh) 2009-01-15 2009-01-15 太阳能光伏-市电混合驱动蓄冷蓄热型热泵机组
PCT/CN2010/070200 WO2010081421A1 (fr) 2009-01-15 2010-01-15 Unité de pompe à chaleur de type à accumulation froid / chaud à entraînement hybride utilisant une alimentation photovoltaïque solaire et une alimentation commerciale

Publications (2)

Publication Number Publication Date
EP2388540A1 true EP2388540A1 (fr) 2011-11-23
EP2388540A4 EP2388540A4 (fr) 2013-07-31

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EP10731055.9A Withdrawn EP2388540A4 (fr) 2009-01-15 2010-01-15 Unite de pompe a chaleur de type a accumulation froid / chaud a entrainement hybride utilisant une alimentation photovoltaique solaire et une alimentation commerciale

Country Status (5)

Country Link
US (1) US20110296865A1 (fr)
EP (1) EP2388540A4 (fr)
CN (1) CN101458005B (fr)
AU (1) AU2010205984A1 (fr)
WO (1) WO2010081421A1 (fr)

Cited By (5)

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WO2016015098A1 (fr) * 2014-07-29 2016-02-04 DI, Shi Appareil, système et procédé de chauffage
FR3072161A1 (fr) * 2017-10-11 2019-04-12 Gerard Llurens Systeme d'echangeurs de chaleur en particulier pour une trigeneration solaire
WO2020254839A1 (fr) * 2019-06-21 2020-12-24 Tsopoulidis Makarios Pompe intermodale de refroidissement, de chauffage et de production d'eau chaude
ES2902039A1 (es) * 2021-12-29 2022-03-24 Vano Josep Francesc Beneyto Nueva aerotermia fotovoltaica
WO2022117959A1 (fr) * 2020-12-03 2022-06-09 Lancey Energy Storage Système thermique incluant une pompe à chaleur comprenant deux types de compresseur

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GB0919934D0 (en) * 2009-11-16 2009-12-30 Sunamp Ltd Energy storage systems
US9093840B2 (en) * 2010-07-02 2015-07-28 Alstom Technology Ltd. System tools for integrating individual load forecasts into a composite load forecast to present a comprehensive synchronized and harmonized load forecast
FR2967761B1 (fr) * 2010-11-19 2014-10-31 Clauger Module d'echange thermique, installation de production de froid et/ou de chaud comprenant ledit module, et procede de production de froid et/ou de chaud a partir de ladite installation
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US8955351B2 (en) * 2012-03-12 2015-02-17 Kunshan Jue-Chung Electronics Co., Ltd. Energy storable air conditioning device
CN103512151A (zh) * 2012-06-29 2014-01-15 株式会社日立制作所 对安装在区域中的空调进行控制的方法和设备
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EP2388540A4 (fr) 2013-07-31
CN101458005A (zh) 2009-06-17

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