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WO2011108068A1 - Système de climatisation et de fourniture d'eau chaude - Google Patents

Système de climatisation et de fourniture d'eau chaude Download PDF

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Publication number
WO2011108068A1
WO2011108068A1 PCT/JP2010/053275 JP2010053275W WO2011108068A1 WO 2011108068 A1 WO2011108068 A1 WO 2011108068A1 JP 2010053275 W JP2010053275 W JP 2010053275W WO 2011108068 A1 WO2011108068 A1 WO 2011108068A1
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WO
WIPO (PCT)
Prior art keywords
hot water
air conditioning
water supply
heat exchanger
refrigerant
Prior art date
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.)
Ceased
Application number
PCT/JP2010/053275
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English (en)
Japanese (ja)
Inventor
智弘 小松
小谷　正直
麻理 内田
陽子 國眼
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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 Hitachi Ltd filed Critical Hitachi Ltd
Priority to CN201080064512.4A priority Critical patent/CN102770725B/zh
Priority to PCT/JP2010/053275 priority patent/WO2011108068A1/fr
Priority to JP2012502911A priority patent/JP5373964B2/ja
Publication of WO2011108068A1 publication Critical patent/WO2011108068A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0096—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater combined with domestic apparatus
    • 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
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/0005—Domestic hot-water supply systems using recuperation of waste heat
    • 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
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/0036—Domestic hot-water supply systems with combination of different kinds of heating means
    • F24D17/0042—Domestic hot-water supply systems with combination of different kinds of heating means recuperated waste heat and 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
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/0036—Domestic hot-water supply systems with combination of different kinds of heating means
    • F24D17/0042—Domestic hot-water supply systems with combination of different kinds of heating means recuperated waste heat and solar energy
    • F24D17/0047—Domestic hot-water supply systems with combination of different kinds of heating means recuperated waste heat and solar energy with accumulation of the heated water
    • 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
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • 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
    • F24D5/00—Hot-air central heating systems; Exhaust gas central heating systems
    • F24D5/12—Hot-air central heating systems; Exhaust gas central heating systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0003—Exclusively-fluid systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0046—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater using natural energy, e.g. solar energy, energy from the ground
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H6/00—Combined water and air heaters
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/12—Heat pump
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/16—Waste heat
    • F24D2200/31—Air conditioning systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0046—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater using natural energy, e.g. solar energy, energy from the ground
    • F24F2005/0064—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater using natural energy, e.g. solar energy, energy from the ground using solar energy
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/13—Hot air central heating systems using heat pumps
    • 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
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/18—Domestic hot-water supply systems using recuperated or waste heat
    • 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
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency

Definitions

  • an air conditioning refrigerant circuit for switching between cooling and heating and a hot water supply refrigerant circuit for hot water supply are mutually exchangeably connected via an intermediate heat exchanger, so that the air conditioning refrigeration cycle and the hot water supply refrigeration circuit are connected.
  • the present invention relates to an air conditioning and hot water supply system in which a binary refrigeration cycle is formed.
  • the air conditioning refrigerant is forced by a natural circulation type cycle in which the air conditioning refrigerant naturally circulates due to density difference
  • the present invention relates to an air-conditioning and hot-water supply system capable of selectively using two air-conditioning refrigeration cycles of a circulating compression type cycle.
  • Patent Document 1 discloses an indoor heat exchanger, an outdoor heat exchanger, a refrigerant pipe, an expansion valve, and another device as a prior art that selectively uses two refrigeration cycles of a natural circulation type cycle and a compression type cycle.
  • a refrigerant natural circulation cooling dehumidifier comprising a refrigerant compression forced circulation device corresponding to the compressor refrigerator of This refrigerant natural circulation cooling dehumidifier is a natural circulation type cycle formed by connecting an outdoor heat exchanger, an indoor heat exchanger located at a lower position than the outdoor heat exchanger, and an expansion valve in an annular manner through a refrigerant pipe.
  • the compression type cycle by the refrigerant compression forced circulation device, and the evaporative heat exchanger of the compression type cycle is closely coupled to the outdoor heat exchanger of the natural circulation type cycle. According to this configuration, since the evaporative heat exchanger can efficiently deprive the outdoor heat exchanger of heat, even if the temperature difference between the indoor and the outdoor is eliminated and the cooling and dehumidifying ability is lowered. The reduction of the cooling dehumidification capacity of the refrigerant natural circulation cooling dehumidifier can be compensated by operating the refrigerant compression forced circulation device.
  • the heat exchanger of the natural circulation type cycle is the heat of the compression type cycle at the peak of air conditioning and heating etc. It was impossible to use as a switch. Therefore, there is a problem that the heat exchange function of the heat exchanger of the natural circulation type cycle is not effectively used. Further, in the above-described conventional technology, when the outside air temperature is equal to or higher than the room temperature, heat is released from the room to the outside air in a compression type cycle, and there is a problem that the heat release is not effectively used. Further, when the outside air temperature is equal to or higher than the dew point temperature in the room, there is a problem that the cooling and dehumidifying can not be performed only by the natural circulation type cycle.
  • the present invention has been made in view of the above-described circumstances, and its first object is to provide an air-conditioning and hot-water supply system capable of utilizing a natural circulation cycle heat exchanger as a compression cycle heat exchanger. It is to do.
  • a second object of the present invention is to provide an air-conditioning and hot-water supply system which can effectively utilize the heat radiation from the compression type cycle.
  • a third object of the present invention is to provide an air-conditioning and hot-water supply system capable of cooling and dehumidifying by a natural circulation type cycle even when the outside air temperature is equal to or higher than the dew point temperature in the room.
  • an air conditioning and hot water supply system circulates an air conditioning refrigerant circuit performing switching between a cooling operation and a heating operation, a hot water supply refrigerant circuit for hot water supply, and the air conditioning refrigerant circuit.
  • An air conditioning and hot water system comprising an intermediate heat exchanger that exchanges heat between an air conditioning refrigerant and a hot water supply refrigerant circulating in the hot water supply refrigerant circuit
  • the air conditioning refrigerant circuit comprising an air conditioning compressor, Air-conditioning use-side heat exchange for heat exchange with the air-conditioning flow path switching valve, the intermediate heat exchanger, the air-conditioning expansion valve, and the heat-carrying medium for air-conditioning use (for example, indoor air, water, or brine)
  • Heaters are sequentially connected by refrigerant piping to form an annular shape, and the hot water supply refrigerant circuit exchanges heat with the hot water supply compressor and the hot water supply use heat transfer medium (for example, water).
  • the expansion valve for hot water supply, and the intermediate heat And a bypass pipe for bypassing the air conditioning compressor, a flow path of the air conditioning refrigerant, a flow path passing through the air conditioning compressor, and the bypass It is characterized in that a bypass opening / closing means for switching to any of the flow paths via piping is provided, and the intermediate heat exchanger is installed at a position higher than the use side heat exchanger for air conditioning.
  • the present invention it is possible to operate by the compression type cycle in which the air conditioning refrigerant is forcibly circulated in the air conditioning refrigerant circuit using the air conditioning compressor, and the intermediate heat exchanger and the air conditioning use side heat exchanger Because of the difference between the heads, it is possible to perform the operation by the natural circulation type cycle using the density difference of the refrigerant for air conditioning by using the bypass piping which bypasses the compressor for air conditioning.
  • one air conditioning refrigerant circuit can constitute both a compression type cycle and a natural circulation type cycle.
  • the present invention can effectively utilize the natural circulation cycle heat exchanger as a compression cycle heat exchanger.
  • power consumption can be reduced by appropriately switching and operating the compression cycle and the natural circulation cycle according to the usage environment.
  • the air conditioning compressor when operated intermittently because the cooling load is small, the power consumption can be significantly reduced by operating the natural circulation type cycle. .
  • the intermediate heat exchanger can perform heat exchange between the air conditioning refrigerant flowing in the air conditioning refrigerant circuit and the hot water supply refrigerant flowing in the hot water supply refrigerant circuit.
  • the intermediate heat exchanger can be used as a condenser in the natural circulation cycle of That is, by releasing the air conditioning refrigerant in the intermediate heat exchanger to the low temperature hot water supply refrigerant flowing into the intermediate heat exchanger, the air conditioning refrigerant can be condensed and liquefied. Therefore, the present invention can secure a large cooling capacity by the natural circulation cycle even if the temperature difference is small.
  • the cooling capacity can not be increased in the natural circulation cycle using the outside air as a heat radiation source, but in the present invention, the intermediate heat exchanger Since heat exchange can be performed between the refrigerant and the air conditioning refrigerant, even when the difference between the outside air temperature and the room temperature is small, the natural circulation type cycle can be reliably operated. That is, the operation of the natural circulation type cycle can be assisted by the heat absorption action of the hot water supply refrigerant flowing through the hot water supply refrigerant circuit.
  • the outside air temperature is equal to or higher than the dew point temperature of the room air
  • cooling and dehumidification of the room air can not be performed only by the natural circulation type cycle.
  • the temperature of the hot water supply refrigerant can be adjusted by appropriately adjusting the opening degree of the expansion valve, the temperature of the air conditioning refrigerant can be lowered to an arbitrary temperature via the intermediate heat exchanger. Therefore, according to the present invention, even when the outside air temperature is equal to or higher than the dew point temperature of the room air, the room can be cooled and dehumidified.
  • the air-conditioning refrigerant circuit exchanges heat between a heat-transfer medium (e.g., the atmosphere) on the heat source side for air-conditioning and the refrigerant for air-conditioning.
  • Heat source side heat exchanger is provided in parallel with the intermediate heat exchanger, and heat exchange is performed between the heat transfer medium on the heat source side heat source side heat transfer medium (for example, the atmosphere) and the hot water supply refrigerant in the hot water supply refrigerant circuit.
  • the heat source side heat exchanger for hot water supply is provided in parallel with the intermediate heat exchanger, and the heat source side heat exchanger for air conditioning is installed at a higher position than the use side heat exchanger for air conditioning .
  • the air conditioning refrigerant circuit and the hot water supply refrigerant circuit can each be operated independently.
  • the operation of the hot water supply cycle by the hot water supply refrigerant circuit is not performed. It is also possible to naturally circulate the air conditioning refrigerant between the heat source side heat exchanger for air conditioning and the use side heat exchanger for air conditioning. Therefore, the present invention can enhance the reduction effect of power consumption.
  • the air-conditioning use-side heat exchanger and an indoor heat exchanger installed in an air-conditioned space are connected by piping.
  • a heat transfer medium circulation circuit is formed, and water or brine as a heat transfer medium of the air conditioning use side is circulated in the air conditioning heat transfer medium circulation circuit.
  • the refrigerant pipe for connecting the indoor unit and the outdoor unit becomes unnecessary as in the prior art, and the amount of refrigerant can be reduced.
  • the natural circulation type cycle is formed in the conventional configuration in which the indoor unit and the outdoor unit are connected by refrigerant piping, it is necessary to install the outdoor unit at a higher position than the indoor unit, which restricts the layout. was there.
  • the heat transfer medium circulation circuit for air conditioning is provided, there is an advantage that the degree of freedom in layout is increased.
  • the hot water supply use heat exchanger is connected to the inlet and the outlet of the hot water supply use heat transfer medium by connecting pipes as the heat transfer medium on the use side.
  • a circuit is formed, and the hot water supply circuit is provided with a tank (for example, a hot water storage tank, a tank called a heat storage tank) capable of storing the heat obtained from the hot water use side heat exchanger. It is characterized.
  • the present invention it is possible to recover the air conditioning exhaust heat and store the heat obtained from the hot water use side heat exchanger in the tank, so that the heat energy can be effectively used and the energy efficiency can be enhanced. Further, since the present invention can store heat in the tank, it is possible to eliminate the difference between the time zone of the air conditioning load and the hot water supply load.
  • the space to be cooled is cooled by the natural circulation type cycle while operating the hot water supply cycle in the daytime where there is a cooling load but no hot water supply load, and the heat stored during the hot water supply cycle operation is stored in the tank. can do.
  • the present invention can boil hot water while cooling in the daytime, and can use the hot water at night.
  • the control device controls the operation of the air conditioning refrigerant circuit and the hot water supply refrigerant circuit, and the control device sets a set room temperature (set by the user). Tr_st), the set humidity (Hr_st) set by the user, the outside air temperature (Toa), and the temperature (Twbi) of the air-conditioning use-side heat exchanger inlet of the air-conditioning use-side heat transfer medium;
  • the air conditioning use side of the heat transport medium for the air conditioning use side determined based on the set room temperature, the set humidity, and the temperature of the air conditioning use side heat exchanger inlet of the air conditioning use side heat transport medium
  • the set temperature (Twb_st) of the heat exchanger outlet, the temperature (Twhi) of the heat use side heat exchanger inlet of the heat transfer medium of the heat use side, the user's request and the heat of the heat use side The temperature of the inlet side of the use-side heat exchanger for the hot water
  • a suitable operation mode can be selected by the control device, a comfortable indoor space can be maintained, and energy saving can be improved.
  • the hot water supply cycle is performed without operating the compressor for the air conditioning cycle.
  • the degree of expansion valve opening makes it possible to produce cold water at any temperature (temperature capable of dehumidifying) by lowering the evaporation temperature. As a result, cooling operation can be performed without operating the air conditioning cycle in a region of low efficiency, and power consumption can be reduced.
  • Operation mode No. of the air conditioning and hot water supply system shown in FIG. 6 is an operation diagram showing flows of the refrigerant and the heat transfer medium in 1;
  • FIG. 7 is an operation diagram showing flows of a refrigerant and a heat transfer medium in 2-1.
  • FIG. 8 is an operation diagram showing flows of a refrigerant and a heat transfer medium in 2-2.
  • FIG. 6 is an operation diagram showing flows of the refrigerant and the heat transfer medium in 3;
  • FIG. 10 is an operation diagram showing flows of a refrigerant and a heat transfer medium in 4-1.
  • Operation mode No. of the air conditioning and hot water supply system shown in FIG. FIG. 7 is an operation diagram showing flows of the refrigerant and the heat transfer medium in 4-2.
  • Operation mode No. of the air conditioning and hot water supply system shown in FIG. FIG. 10 is an operation diagram showing flows of the refrigerant and the heat transfer medium at 5; It is the figure which showed the selection conditions of each operation mode of the air-conditioning and hot water supply system shown in FIG. FIG.
  • FIG. 10 (a) is a pressure-enthalpy diagram of the refrigerant in the air conditioning and hot water supply system according to the first embodiment of the present invention
  • FIG. 2. is a pressure-enthalpy diagram of the refrigerant in the conventional air conditioning and hot water supply system. It is a systematic diagram of the air-conditioning and hot water supply system which concerns on the example of the 2nd Embodiment of this invention. It is a systematic diagram of the air-conditioning and hot water supply system which concerns on the example of the 3rd Embodiment of this invention.
  • the air conditioning and hot water supply system is an air conditioning refrigerant circuit 5 that operates by switching between a cooling operation and a heating operation, and a hot water supply refrigerant circuit that performs hot water supply. 6, heat exchange with the air conditioning refrigerant circuit 5 to exchange heat with the air conditioning cold / hot water circulation circuit (air conditioning heat transfer medium circulation circuit) 8 for air conditioning the room of the house 60 and the hot water supply refrigerant circuit 6 And a hot water supply circuit 9 for supplying hot water.
  • the air-conditioning and hot-water supply system according to the first embodiment of the present invention has a unit configuration including a heat pump unit 1 disposed outside the room and an indoor unit 2 disposed inside the room.
  • an air conditioning refrigerant circuit 5 a hot water supply refrigerant circuit 6, an air conditioning cold and hot water circulation circuit 8 and a hot water supply circuit 9 are incorporated. Furthermore, an intermediate heat exchanger 23 is disposed between the air conditioning refrigerant circuit 5 and the hot water supply refrigerant circuit 6.
  • the intermediate heat exchanger 23 has a structure capable of exchanging heat between the air conditioning refrigerant circulating in the air conditioning refrigerant circuit 5 and the hot water supply refrigerant circulating in the hot water supply refrigerant circuit 6.
  • the air conditioning refrigerant circuit 5 is a circuit in which a refrigeration cycle is formed by circulating the air conditioning refrigerant, and the air conditioning compressor 21 for compressing the air conditioning refrigerant, a four-way valve for switching the air conditioning refrigerant flow path (for air conditioning (Flow path switching valve) 22, intermediate heat exchanger 23, heat source side heat exchanger 24 for air conditioning which exchanges heat with the atmosphere sent by a fan (not shown), depressurizing refrigerant tank 26 for air conditioning, refrigerant for air conditioning
  • the air conditioning expansion valve 27 and the air conditioning use-side heat exchanger 28 performing heat exchange with the air conditioning hot and cold water circulation circuit 8 are connected by refrigerant pipes and formed annularly.
  • the intermediate heat exchanger 23 is installed at a position higher than the use side heat exchanger 28 for air conditioning, and a head difference is formed between the intermediate heat exchanger 23 and the use side heat exchanger 28 for air conditioning. ing. Due to this head difference, the air conditioning refrigerant can be naturally circulated in the air conditioning refrigerant circuit 5 (details will be described later).
  • the air-conditioning refrigerant circuit 5 first includes the discharge port 21b of the air-conditioning compressor 21, the four-way valve 22, the intermediate heat exchanger 23, the air-conditioning refrigerant tank 26, the air-conditioning expansion valve 27, the air-conditioning use side heat exchanger 28,
  • the air-conditioning refrigerant main circuit 5a is formed in an annular shape by connecting the four-way valve 22 and the suction port 21a of the air-conditioning compressor 21 in the order of the refrigerant pipe.
  • the air conditioning refrigerant circuit 5 is configured such that two air conditioning refrigerant branch paths 5b and 5c are provided in the air conditioning refrigerant main circuit 5a.
  • the first air conditioning refrigerant branch path 5b is an air conditioning refrigerant branch path passing through the air conditioning heat source side heat exchanger 24 connected in parallel with the intermediate heat exchanger 23, and specifically, the four-way valve 22 and Branch from the branch point I located between the intermediate heat exchanger 23 and the branch between the intermediate heat exchanger 23 and the air conditioning refrigerant tank 26 via the air conditioning heat source side heat exchanger 24 It is a refrigerant branch path for air conditioning joined at point J.
  • the second air conditioning refrigerant branch path 5c is an air conditioning refrigerant branch path that bypasses the suction port 21a and the discharge port 21b of the air conditioning compressor 21, and more specifically, the air conditioning use side heat exchanger 28 and Air conditioning formed by connecting a branch point A at a position between the four-way valve 22 and a branch point B at a position between the four-way valve 22 and the branch point I by a refrigerant bypass pipe (bypass pipe) 29 for air conditioning Refrigerant branch.
  • a three-way valve 34a is provided at the branch point A, and a three-way valve 34b is provided at the branch point B.
  • two-way valves 35 a and 35 b are provided to sandwich the intermediate heat exchanger 23, and two-way valves 35 c and 35 d are provided to sandwich the heat source side heat exchanger 24 for air conditioning.
  • the air conditioning refrigerant circulating in the air conditioning refrigerant circuit 5 for example, R410a, R134a, HFO1234yf, HFO1234ze, CO2 can be used.
  • the air conditioning compressor 21 is a variable displacement compressor capable of capacity control.
  • a piston type, a rotary type, a scroll type, a screw type, or a centrifugal type can be employed.
  • the air conditioning compressor 21 is a scroll compressor, and capacity control is possible by inverter control, and the rotational speed is variable from low speed to high speed.
  • the air conditioning refrigerant heat transfer pipe in which the air conditioning refrigerant flows and the hot water supply refrigerant heat transfer pipe in which the hot water supply refrigerant flows are in thermal contact with each other (for example, heat transfer pipes are joined) ) Is a heat exchanger integrally configured.
  • the air-conditioning use-side heat exchanger 28 is not shown, the air-conditioning refrigerant heat transfer pipe through which the air-conditioning refrigerant flows and the air-conditioning cold / hot water heat transfer pipe through which water (heat transfer medium on the air-conditioning use side) flows are thermally It is configured to contact the.
  • the air conditioning refrigerant tank 26 functions as a buffer that controls the amount of the air conditioning refrigerant that changes by switching the flow path.
  • the air conditioning expansion valve 27 can reduce the pressure of the air conditioning refrigerant to a predetermined pressure by adjusting the opening degree of the valve.
  • the air conditioning cold / hot water circulation circuit (air conditioning heat transfer medium circulation circuit) 8 is a circuit through which water flows as a heat transfer medium of the air conditioning use side for heat exchange with the air conditioning refrigerant circuit 5.
  • the indoor heat exchanger 61 installed in the 60, the air conditioning cold and hot water circulation pump 52, the four-way valve 53, and the air conditioning use side heat exchanger 28 are sequentially connected by the air conditioning hot and cold water piping, and a circuit formed annularly is there.
  • the water (cold water or hot water) flowing in the air conditioning cold / hot water circulation circuit 8 exchanges heat with the air in the house 60 via the indoor heat exchanger 61 to cool or heat the inside of the house 60.
  • brine such as ethylene glycol
  • cold water or “hot water” may be used as water flowing through the air conditioning cold / hot water circulation circuit 8 but “cold water” means water flowing through the air conditioning cold / hot water circulation circuit 8 during cooling.
  • hot water is used in the meaning of water flowing through the air conditioning cold and hot water circulation circuit 8 at the time of heating.
  • the hot water supply refrigerant circuit 6 is a circuit in which a refrigeration cycle is formed by circulation of the hot water supply refrigerant, and the hot water supply compressor 41 for compressing the hot water supply refrigerant and the hot water use side heat exchanging heat with the hot water supply circuit 9 Exchanger 42, a hot water supply refrigerant tank 46, a hot water supply expansion valve 43 for depressurizing hot water supply refrigerant, an intermediate heat exchanger 23, and a hot water supply heat source side which exchanges heat with the atmosphere sent by a fan (not shown)
  • the heat exchanger 44 is connected by a refrigerant pipe to form an annular shape.
  • the hot water supply refrigerant circuit 6 includes the discharge port 41b of the hot water supply compressor 41, the hot water use side heat exchanger 42, the hot water supply refrigerant tank 46, the hot water expansion valve 43, the intermediate heat exchanger 23, and the hot water use compressor.
  • the hot water supply refrigerant main circuit 6a is formed in an annular shape by connecting in order of the suction port 41a of 41 with a refrigerant pipe.
  • the hot water supply refrigerant circuit 6 is configured by providing the hot water supply refrigerant branch path 6b in the hot water supply refrigerant main circuit 6a.
  • the hot water supply refrigerant branch path 6b is a hot water supply refrigerant branch path via the hot water supply heat source side heat exchanger 44 connected in parallel with the intermediate heat exchanger 23, and specifically, the hot water supply expansion valve 43 and the intermediate temperature It branches from the branch point K located at a position between the heat exchangers 23 and is located between the intermediate heat exchanger 23 and the suction port 41 a of the hot water supply compressor 41 via the hot water supply heat source side heat exchanger 44.
  • This is a hot water supply refrigerant branch path that joins at a certain branch point L.
  • a two-way valve 49 b is provided near the inlet of the intermediate heat exchanger 23, and a two-way valve 49 a is provided near the inlet of the heat source side heat exchanger for hot water supply 44.
  • the hot water supply refrigerant circulating through the hot water supply refrigerant circuit 6, for example, R134a, HFO1234yf, HFO1234ze, CO2 can be used.
  • the hot water supply compressor 41 can perform capacity control by inverter control, and has a variable rotational speed from low speed to high speed.
  • the hot water use heat exchanger 42 is configured such that the hot water supply heat transfer pipe through which the water supplied to the hot water supply circuit 9 flows thermally contacts the hot water supply refrigerant heat transfer pipe through which the hot water supply refrigerant flows. It is done.
  • the hot water supply expansion valve 43 can reduce the pressure of the hot water supply refrigerant to a predetermined pressure by adjusting the opening degree of the valve.
  • the hot water supply circuit 9 is formed by connecting one end of the hot water supply pipe 72 to the inlet of the hot water use side heat exchanger 42 and connecting one end of the hot water supply pipe 73 to the hot water use side heat exchanger 42. It is a circuit.
  • the other end of the hot water supply pipe 72 is connected to a water supply source, and the other end of the hot water supply pipe 73 is connected to a device (such as a bathtub) on the hot water supply load side. Therefore, the water supplied into the hot water supply circuit 9 becomes hot water by heat exchange with the hot water use side heat exchanger 42, and is introduced to the hot water supply load side device while flowing through the hot water supply pipe 73.
  • the hot water supply circuit 9 incorporates a hot water supply circulation pump and a hot water supply flow rate sensor for detecting the flow rate of water.
  • the flow of the hot water supply refrigerant and the flow of water are opposite to each other.
  • the air conditioning and hot water supply system is provided with a plurality of temperature sensors TE1 to TE8.
  • the temperature sensor T1 is at the inlet (inlet at the time of cooling operation) of the use side heat exchanger 28 for air conditioning, and the temperature sensor TE2 is at the outlet (outlet during the cooling operation).
  • a temperature sensor TE3 is provided at the suction port 21a of the air conditioning compressor 21, and a temperature sensor TE4 is provided at the discharge port 21b.
  • a temperature sensor TE7 is provided at the inlet of the hot water use side heat exchanger 42, and a temperature sensor TE8 is provided at the outlet.
  • an outside air temperature sensor for measuring the outside air temperature is also provided.
  • Control device 1a receives a command signal from a remote controller (not shown), detection signals of temperature sensors TE1 to TE8 and an outside air temperature sensor, and the like, and based on these input signals, air conditioner compressor 21 and hot water supply compressor 41 Drive / stop, switching of the four-way valves 22, 53, adjustment of the opening degree of the air conditioning expansion valve 27 and the hot water supply expansion valve 43, switching of the three-way valves 34a, 34b, drive / stop of the air conditioning hot and cold water circulation pump 52, The control necessary for the operation of the air conditioning and hot water supply system is performed in opening and closing of the two-way valves 35a to 35d and the two-way valves 49a and 49b.
  • FIGS. 2-8 the arrows attached to the heat exchanger indicate the flow of heat, and the arrows attached to the circuits 5, 6, 8 and 9 indicate the direction in which the fluid flows through the circuits. There is. Also, in FIGS. 2-8, for the two-way valve, it is shown that the one painted black is in the closed state, and for the three-way valve it is shown that the port painted black is closed. For the four-way valve, it indicates that the solid flow path is effective. In FIGS. 2 to 8, the temperature sensors TE1 to TE8 are not shown.
  • Operation mode No. 1 ⁇ cooling / hot-water supply operation>
  • Operation mode No. Reference numeral 1 denotes an operation mode in which the cooling operation by the air conditioning refrigerant circuit 5 and the hot water supply operation by the hot water supply refrigerant circuit 6 are performed.
  • the high temperature and high pressure gas refrigerant discharged from the discharge port 21 b of the air conditioning compressor 21 flows into the air conditioning heat source side heat exchanger 24 through the four-way valve 22.
  • the high-temperature, high-pressure gas refrigerant flowing in the air-conditioning heat source side heat exchanger 24 dissipates heat to the atmosphere, condenses, and liquefies.
  • the high pressure refrigerant is decompressed and expanded by the air conditioning expansion valve 27 adjusted to a predetermined opening degree, becomes a low temperature low pressure gas-liquid two-phase refrigerant, and flows into the air conditioning use side heat exchanger 28.
  • the gas-liquid two-phase refrigerant flowing in the air-conditioning use-side heat exchanger 28 absorbs heat from the cold water flowing in the air-conditioning cold / hot water circulation circuit 8 and evaporates to become a low-pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the suction port 21a of the air conditioning compressor 21 through the four-way valve 22, and is compressed again by the air conditioning compressor 21 to be a high temperature high pressure gas refrigerant.
  • Operation mode No. In 1 the two-way valves 35a and 35b before and after the intermediate heat exchanger 23 are closed so that the air conditioning refrigerant does not flow in the intermediate heat exchanger 23. Further, the second air conditioning refrigerant branch path 5c that bypasses the air conditioning compressor 21 is closed by the three-way valves 34a and 34b before and after the air conditioning compressor 21.
  • the cold water radiated to the air conditioning refrigerant flowing through the air conditioning use-side heat exchanger 28 passes through the air conditioning cold and hot water piping by driving the air conditioning hot and cold water circulation pump 52 It flows into the exchanger 61.
  • the indoor heat exchanger 61 heat exchange is performed between the cold water in the air conditioning cold and hot water circulation circuit 8 and the high temperature air in the house 60, and the air of the house 60 is cooled. That is, the room of the house 60 is cooled. At this time, the cold water flowing through the indoor heat exchanger 61 absorbs heat from the air in the house 60 and is heated.
  • the heated cold water circulates in the air conditioning cold / hot water circulation circuit 8 by the air conditioning cold / hot water circulation pump 52 and exchanges heat with the air conditioning refrigerant circuit 5 while flowing through the air conditioning use side heat exchanger 28 again. , Is cooled to a predetermined temperature.
  • the gas refrigerant compressed by the hot water supply compressor 41 and brought to a high temperature and high pressure flows into the hot water supply use side heat exchanger 42.
  • the high-temperature, high-pressure gas refrigerant flowing in the hot water use side heat exchanger 42 dissipates heat to the water flowing in the hot water supply circuit 9, condenses and liquefies.
  • the supplied water becomes hot water of a predetermined temperature by receiving the heat from the hot water supply refrigerant circuit 6 by the hot water supply use side heat exchanger 42.
  • the liquefied high-pressure refrigerant is decompressed and expanded by the hot water supply expansion valve 43 adjusted to a predetermined opening degree, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant absorbs heat from the atmosphere and evaporates to become a low-pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the suction port 41a of the hot water supply compressor 41, is compressed again by the hot water supply compressor 41, and becomes a high temperature and high pressure gas refrigerant.
  • Operation mode No. 2-1 is an operation mode performed when exhaust heat in the cooling operation is larger than heat absorption in the hot water supply operation among modes in which the hot water supply operation is performed using exhaust heat from the cooling operation.
  • the high temperature and high pressure gas refrigerant discharged from the discharge port 21b of the air conditioning compressor 21 passes through the four-way valve 22 and is divided into the air conditioning heat source side heat exchanger 24 and the intermediate heat exchanger 23. Flow in. That is, the gas refrigerant branches and flows to the air conditioning refrigerant main circuit 5a and the first air conditioning refrigerant branch path 5b.
  • the high-temperature, high-pressure gas refrigerant flowing in the air-conditioning heat source side heat exchanger 24 dissipates heat to the atmosphere, condenses, and liquefies.
  • the high-temperature and high-pressure gas refrigerant flowing in the intermediate heat exchanger 23 is condensed and liquefied by radiating heat to the hot-water supply refrigerant flowing in the hot-water supply circuit 6. That is, in the intermediate heat exchanger 23, heat exchange is performed between the air conditioning refrigerant and the hot water supply refrigerant.
  • the high-pressure refrigerant that has flowed out from the air conditioning heat source side heat exchanger 24 and the intermediate heat exchanger 23 is decompressed and expanded by the air conditioning expansion valve 27 adjusted to a predetermined opening degree, and a low temperature low pressure gas-liquid two-phase refrigerant And flows into the air-conditioning use-side heat exchanger 28.
  • the gas-liquid two-phase refrigerant flowing in the air-conditioning use-side heat exchanger 28 absorbs heat from the cold water flowing in the air-conditioning cold / hot water circulation circuit 8 and evaporates to become a low-pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the suction port 21a of the air conditioning compressor 21 through the four-way valve 22, and is compressed again by the air conditioning compressor 21 to be a high temperature high pressure gas refrigerant.
  • the cold water radiated to the air conditioning refrigerant flowing through the air conditioning use-side heat exchanger 28 passes through the air conditioning cold and hot water piping by driving the air conditioning hot and cold water circulation pump 52 It flows into the exchanger 61.
  • the indoor heat exchanger 61 heat exchange is performed between the cold water in the air conditioning cold and hot water circulation circuit 8 and the high temperature air in the house 60, and the air of the house 60 is cooled. That is, the room of the house 60 is cooled. At this time, the cold water flowing through the indoor heat exchanger 61 absorbs heat from the air in the house 60 and is heated.
  • the heated cold water circulates in the air conditioning cold / hot water circulation circuit 8 by the air conditioning cold / hot water circulation pump 52 and exchanges heat with the air conditioning refrigerant circuit 5 while flowing through the air conditioning use side heat exchanger 28 again. , Is cooled to a predetermined temperature.
  • the gas refrigerant compressed by the hot water supply compressor 41 and brought to a high temperature and high pressure flows into the hot water supply use side heat exchanger 42.
  • the high-temperature, high-pressure gas refrigerant flowing in the hot water use side heat exchanger 42 dissipates heat to the water flowing in the hot water supply circuit 9, condenses and liquefies.
  • the supplied water becomes hot water of a predetermined temperature by receiving the heat from the hot water supply refrigerant circuit 6 by the hot water supply use side heat exchanger 42.
  • the liquefied high-pressure refrigerant is decompressed and expanded by the hot water supply expansion valve 43 to become a low temperature low pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant absorbs heat from the air conditioning refrigerant and evaporates to become a low pressure gas refrigerant. That is, in the intermediate heat exchanger 23, heat exchange is performed between the air conditioning refrigerant and the hot water supply refrigerant.
  • the low pressure gas refrigerant flows into the suction port 41a of the hot water supply compressor 41, is compressed again by the hot water supply compressor 41, and becomes a high temperature and high pressure gas refrigerant.
  • This operation mode No. In 2-1 the intermediate heat exchanger 23 in the hot water supply refrigerant circuit 6 functions as an evaporator using the exhaust heat of the air conditioning refrigerant circuit 5.
  • This operation mode No. In 2-1 since the hot water supply cycle operation can be performed by the hot water supply refrigerant circuit 6 using the exhaust heat generated in the cooling operation of the air conditioning refrigerant circuit 5, effective use of energy can be achieved. Moreover, this operation mode No. In 2-1, since the air conditioning exhaust heat is used as a heat source, the evaporation temperature of the hot water supply cycle can be raised as compared with the case where outside air is used as a heat source. Therefore, the operation mode No. In 2-1, since the input to the hot water supply compressor 41 can be reduced, the power consumption of the hot water supply compressor 41 can be reduced. Furthermore, operation mode No. In 2-1, since the fan of the heat source side heat exchanger 44 for hot water supply can be stopped, the power consumption concerning operation of a hot-water supply cycle is reduced.
  • Operation mode No. 2-2 is an operation mode performed when the exhaust heat in the cooling operation is smaller than the heat absorption in the hot water supply operation among the modes in which the hot water supply operation is performed using the exhaust heat in the cooling operation.
  • This operation mode No. Since 2-2 is a mode performed when the exhaust heat by the cooling operation is smaller than the heat absorption by the hot water supply operation, it is not necessary to use the heat source side heat exchanger 24 for air conditioning. Therefore, the two-way valves 35c and 35d before and after the heat source side heat exchanger 24 for air conditioning are closed so that the refrigerant for air conditioning does not flow in the heat source side heat exchanger 24 for air conditioning.
  • the high temperature and high pressure gas refrigerant discharged from the discharge port 21 b of the air conditioning compressor 21 flows into the intermediate heat exchanger 23 through the four-way valve 22.
  • the high-temperature, high-pressure gas refrigerant flowing in the intermediate heat exchanger 23 is condensed and liquefied by radiating heat to the hot-water supply refrigerant flowing in the hot-water supply circuit 6. That is, in the intermediate heat exchanger 23, heat exchange is performed between the air conditioning refrigerant and the hot water supply refrigerant.
  • the high-pressure refrigerant is decompressed and expanded by the air conditioning expansion valve 27 adjusted to a predetermined opening degree, turns into a low temperature low pressure gas-liquid two-phase refrigerant, and flows into the air conditioning use side heat exchanger 28.
  • the gas-liquid two-phase refrigerant flowing in the air-conditioning use-side heat exchanger 28 absorbs heat from the cold water flowing in the air-conditioning cold / hot water circulation circuit 8 and evaporates to become a low-pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the suction port 21a of the air conditioning compressor 21 through the four-way valve 22, and is compressed again by the air conditioning compressor 21 to be a high temperature high pressure gas refrigerant.
  • the cold water radiated to the air conditioning refrigerant flowing through the air conditioning use-side heat exchanger 28 passes through the air conditioning cold and hot water piping by driving the air conditioning hot and cold water circulation pump 52 It flows into the exchanger 61.
  • the indoor heat exchanger 61 heat exchange is performed between the cold water in the air conditioning cold and hot water circulation circuit 8 and the high temperature air in the house 60, and the air of the house 60 is cooled. That is, the room of the house 60 is cooled. At this time, the cold water flowing through the indoor heat exchanger 61 absorbs heat from the air in the house 60 and is heated.
  • the heated cold water circulates in the air conditioning cold / hot water circulation circuit 8 by the air conditioning cold / hot water circulation pump 52 and exchanges heat with the air conditioning refrigerant circuit 5 while flowing through the air conditioning use side heat exchanger 28 again. , Is cooled to a predetermined temperature.
  • the gas refrigerant compressed by the hot water supply compressor 41 and brought to a high temperature and high pressure flows into the hot water supply use side heat exchanger 42.
  • the high-temperature, high-pressure gas refrigerant flowing in the hot water use side heat exchanger 42 dissipates heat to the water flowing in the hot water supply circuit 9, condenses and liquefies.
  • the supplied water becomes hot water of a predetermined temperature by receiving the heat from the hot water supply refrigerant circuit 6 by the hot water supply use side heat exchanger 42.
  • the liquefied high-pressure refrigerant is decompressed and expanded by the hot water supply expansion valve 43 to become a low temperature low pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant is divided into the heat source side heat exchanger for hot water supply 44 and the intermediate heat exchanger 23 and flows in. That is, the gas refrigerant branches into the hot water supply refrigerant main circuit 6a and the hot water supply refrigerant branch path 6b and flows.
  • the gas-liquid two-phase refrigerant flowing in the heat source side heat exchanger for hot water supply 44 absorbs heat from the atmosphere and evaporates to be a low pressure gas refrigerant.
  • the gas-liquid two-phase refrigerant flowing in the intermediate heat exchanger 23 absorbs heat from the air conditioning refrigerant flowing in the air conditioning circuit 5, evaporates, and becomes a low pressure gas refrigerant. That is, in the intermediate heat exchanger 23, heat exchange is performed between the air conditioning refrigerant and the hot water supply refrigerant.
  • the low-pressure gas refrigerant that has flowed out of each of the heat source side heat exchanger 44 for hot water supply and the intermediate heat exchanger 23 flows into the suction port 41 a of the hot water supply compressor 41 and is compressed again by the hot water supply compressor 41. It becomes a gas refrigerant.
  • the intermediate heat exchanger 23 in the hot water supply refrigerant circuit 6 functions as an evaporator using the exhaust heat of the air conditioning refrigerant circuit 5.
  • This operation mode No. In 2-2 since the air conditioning exhaust heat generated in the cooling operation of the air conditioning refrigerant circuit 5 can be dissipated to the hot water supply refrigerant circuit 6, the condensation of the air conditioning cycle is performed compared to the heat dissipation of the air conditioning exhaust heat. Since the pressure can be reduced, the input of the air conditioning compressor 21 can be reduced. Therefore, the operation mode No. In 2-2, the power consumption of the air conditioning compressor 21 can be reduced. Furthermore, operation mode No. In 2-2, since the fan of the heat source side heat exchanger 24 for air conditioning can be stopped, the power consumption concerning operation of an air conditioning cycle is reduced.
  • Operation mode No. 3 is a mode in which the heating operation by the air conditioning refrigerant circuit 5 and the hot water supply operation by the hot water supply refrigerant circuit 6 are performed.
  • the high temperature and high pressure gas refrigerant discharged from the discharge port 21 b of the air conditioning compressor 21 flows through the four-way valve 22 into the air conditioning use side heat exchanger 28.
  • the high-temperature and high-pressure gas refrigerant flowing in the air-conditioning use side heat exchanger 28 dissipates heat to the hot water flowing in the air-conditioning hot and cold water circuit 8, condenses, and liquefies.
  • the high-pressure refrigerant is decompressed and expanded by the air conditioning expansion valve 27 adjusted to a predetermined opening degree, becomes a low temperature low pressure gas-liquid two-phase refrigerant, and flows into the air conditioning heat source side heat exchanger 24.
  • the gas-liquid two-phase refrigerant flowing in the heat source-side heat exchanger 24 for air conditioning absorbs heat from the atmosphere and evaporates to be a low pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the suction port 21a of the air conditioning compressor 21 through the four-way valve 22, and is compressed again by the air conditioning compressor 21 to be a high temperature high pressure gas refrigerant.
  • hot water absorbed from the air conditioning refrigerant flowing through the air conditioning use-side heat exchanger 28 passes through the air conditioning cold / hot water piping by driving the air conditioning cold / hot water circulation pump 52 It flows into the exchanger 61.
  • the indoor heat exchanger 61 heat exchange is performed between the hot water in the air conditioning cold and hot water circulation circuit 8 and the low temperature air in the house 60, and the air of the house 60 is heated. That is, the room of the house 60 is heated. At this time, the hot water flowing through the indoor heat exchanger 61 dissipates heat to the air in the house 60 and is cooled.
  • the cooled hot water circulates in the air conditioning cold and hot water circulation circuit 8 by the air conditioning cold and hot water circulation pump 52, and exchanges heat with the air conditioning refrigerant circuit 5 while flowing through the air conditioning use side heat exchanger 28 again.
  • the temperature is raised to a predetermined temperature.
  • the gas refrigerant compressed by the hot water supply compressor 41 and brought to a high temperature and high pressure flows into the hot water supply use side heat exchanger 42.
  • the high-temperature, high-pressure gas refrigerant flowing in the hot water use side heat exchanger 42 dissipates heat to the water flowing in the hot water supply circuit 9, condenses and liquefies.
  • the supplied water becomes hot water of a predetermined temperature by receiving the heat from the hot water supply refrigerant circuit 6 by the hot water supply use side heat exchanger 42.
  • the liquefied high-pressure refrigerant is decompressed and expanded by the hot water supply expansion valve 43 adjusted to a predetermined opening degree, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant absorbs heat from the atmosphere and evaporates to become a low-pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the suction port 41a of the hot water supply compressor 41, is compressed again by the hot water supply compressor 41, and becomes a high temperature and high pressure gas refrigerant.
  • Operation mode No. 4-1 is an operation mode in which the air conditioning refrigerant in the air conditioning refrigerant circuit 5 is naturally circulated while the hot water supply operation by the hot water supply refrigerant circuit 6 is performed to perform the cooling operation. It is an operation mode performed when larger.
  • This operation mode No. In 4-1 the air conditioning compressor 21 is stopped, and the second air conditioning refrigerant branch passage 5c for bypassing the air conditioning compressor 21 is opened by the three-way valves 34a and 34b before and after the air conditioning compressor 21. And the path (path indicated by the dotted line in FIG. 6) passing through the air conditioning compressor 21 is closed. Therefore, the air conditioning refrigerant bypasses the air conditioning compressor 21 and circulates in the air conditioning refrigerant circuit 5.
  • Operation mode No. In 4-1 the two-way valves 35a and 35b before and after the intermediate heat exchanger 23 are open.
  • the air conditioning expansion valve 27 is adjusted to a predetermined opening degree in accordance with the amount of heat exchange desired to be obtained by the air conditioning use-side heat exchanger 28.
  • the air conditioning refrigerant accumulated in the intermediate heat exchanger 23 releases heat to the hot water supply refrigerant flowing through the hot water supply refrigerant circuit 6, condenses, and condenses.
  • the liquid refrigerant with a large density descends under the influence of gravity, passes through the expansion valve 27 for air conditioning, and flows through the air conditioning hot and cold water circulation circuit 8 while flowing through the air conditioning use heat exchanger 28 It absorbs heat and evaporates to gasify. At this time, the evaporated refrigerant flows toward the intermediate heat exchanger 23 because a pressure gradient is generated due to the density difference of the refrigerant.
  • the air conditioning refrigerant accumulated in the heat source side heat exchanger 24 for air conditioning is thermally radiated to the atmosphere, condensed, and liquefied to perform natural circulation in the air conditioning refrigerant circuit 5 due to the density difference. It will be Thus, the natural circulation cycle in which the air conditioning refrigerant naturally circulates is formed in the air conditioning refrigerant circuit 5.
  • the cold water radiated to the air conditioning refrigerant flowing through the air conditioning use-side heat exchanger 28 passes through the air conditioning cold and hot water piping by driving the air conditioning hot and cold water circulation pump 52 It flows into the exchanger 61.
  • the indoor heat exchanger 61 heat exchange is performed between the cold water in the air conditioning cold and hot water circulation circuit 8 and the high temperature air in the house 60, and the air of the house 60 is cooled. That is, the room of the house 60 is cooled. At this time, the cold water flowing through the indoor heat exchanger 61 absorbs heat from the air in the house 60 and is heated.
  • the heated cold water circulates in the air conditioning cold / hot water circulation circuit 8 by the air conditioning cold / hot water circulation pump 52 and exchanges heat with the air conditioning refrigerant circuit 5 while flowing through the air conditioning use side heat exchanger 28 again. , Is cooled to a predetermined temperature.
  • the gas refrigerant compressed by the hot water supply compressor 41 and brought to a high temperature and high pressure flows into the hot water supply use side heat exchanger 42.
  • the high-temperature, high-pressure gas refrigerant flowing in the hot water use side heat exchanger 42 dissipates heat to the water flowing in the hot water supply circuit 9, condenses and liquefies.
  • the supplied water becomes hot water of a predetermined temperature by receiving the heat from the hot water supply refrigerant circuit 6 by the hot water supply use side heat exchanger 42.
  • the liquefied high-pressure refrigerant is decompressed and expanded by the hot water supply expansion valve 43 to become a low temperature low pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant absorbs heat from the air conditioning refrigerant and evaporates to become a low pressure gas refrigerant. That is, in the intermediate heat exchanger 23, heat exchange is performed between the air conditioning refrigerant and the hot water supply refrigerant.
  • the low pressure gas refrigerant flows into the suction port 41a of the hot water supply compressor 41, is compressed again by the hot water supply compressor 41, and becomes a high temperature and high pressure gas refrigerant.
  • the intermediate heat exchanger 23 in the hot water supply refrigerant circuit 6 functions as an evaporator utilizing the heat of the air conditioning refrigerant which naturally circulates in the air conditioning refrigerant circuit 5.
  • the natural circulation of the air conditioning refrigerant is assisted by the heat (cool heat) of the hot water supply refrigerant obtained by the hot water supply operation. Therefore, the efficiency of cooling by natural circulation of the air conditioning refrigerant is improved, and the inside of the house 60 becomes comfortable.
  • Operation mode No. 4-2 Air conditioning side natural circulation operation using the hot water supply cycle>
  • Operation mode No. 4-2 in the mode of performing the cooling operation by naturally circulating the air conditioning refrigerant in the air conditioning refrigerant circuit 5 while performing the hot water supply operation by the hot water supply refrigerant circuit 6, the exhaust heat by the cooling operation is more than the heat absorption by the hot water supply operation. It is an operation mode performed when it is small.
  • the path (the path shown by the dotted line in FIG. 7) passing through the air conditioning compressor 21 is closed. Therefore, the air conditioning refrigerant bypasses the air conditioning compressor 21 and circulates in the air conditioning refrigerant circuit 5.
  • the air conditioning expansion valve 27 is adjusted to a predetermined opening degree in accordance with the amount of heat exchange desired to be obtained by the air conditioning use-side heat exchanger 28.
  • the air conditioning refrigerant accumulated in the intermediate heat exchanger 23 releases heat to the hot water supply refrigerant flowing through the hot water supply refrigerant circuit 6, condenses, and condenses.
  • the liquid refrigerant with a large density descends under the influence of gravity, passes through the expansion valve 27 for air conditioning, and flows through the air conditioning hot and cold water circulation circuit 8 while flowing through the air conditioning use heat exchanger 28 It absorbs heat and evaporates to gasify. At this time, the evaporated refrigerant flows toward the intermediate heat exchanger 23 because a pressure gradient is generated due to the density difference of the refrigerant.
  • the air conditioning refrigerant circuit 5 is formed with a natural circulation cycle in which the air conditioning refrigerant naturally circulates.
  • the cold water radiated to the air conditioning refrigerant flowing through the air conditioning use-side heat exchanger 28 passes through the air conditioning cold and hot water piping by driving the air conditioning hot and cold water circulation pump 52 It flows into the exchanger 61.
  • the indoor heat exchanger 61 heat exchange is performed between the cold water in the air conditioning cold and hot water circulation circuit 8 and the high temperature air in the house 60, and the air of the house 60 is cooled. That is, the room of the house 60 is cooled. At this time, the cold water flowing through the indoor heat exchanger 61 absorbs heat from the air in the house 60 and is heated.
  • the heated cold water circulates in the air conditioning cold / hot water circulation circuit 8 by the air conditioning cold / hot water circulation pump 52 and exchanges heat with the air conditioning refrigerant circuit 5 while flowing through the air conditioning use side heat exchanger 28 again. , Is cooled to a predetermined temperature.
  • the gas refrigerant compressed by the hot water supply compressor 41 and brought to a high temperature and high pressure flows into the hot water supply use side heat exchanger 42.
  • the high-temperature, high-pressure gas refrigerant flowing in the hot water use side heat exchanger 42 dissipates heat to the water flowing in the hot water supply circuit 9, condenses and liquefies.
  • the supplied water becomes hot water of a predetermined temperature by receiving the heat from the hot water supply refrigerant circuit 6 by the hot water supply use side heat exchanger 42.
  • the liquefied high-pressure refrigerant is decompressed and expanded by the hot water supply expansion valve 43 to become a low temperature low pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant is divided into the intermediate heat exchanger 23 and the heat source side heat exchanger 44 for hot water supply and flows.
  • the gas-liquid two-phase refrigerant that has flowed through the intermediate heat exchanger 23 absorbs heat from the air conditioning refrigerant and is evaporated to become a low pressure gas refrigerant. That is, in the intermediate heat exchanger 23, heat exchange is performed between the air conditioning refrigerant and the hot water supply refrigerant. Further, the gas-liquid two-phase refrigerant that has flowed through the heat source side heat exchanger for hot water supply 44 also absorbs heat from the atmosphere and evaporates to become a low pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the suction port 41a of the hot water supply compressor 41, is compressed again by the hot water supply compressor 41, and becomes a high temperature and high pressure gas refrigerant.
  • the intermediate heat exchanger 23 in the hot water supply refrigerant circuit 6 functions as an evaporator utilizing the heat of the air conditioning refrigerant which naturally circulates in the air conditioning refrigerant circuit 5.
  • the natural circulation of the air conditioning refrigerant is assisted by the heat (cool heat) of the hot water supply refrigerant obtained by the hot water supply operation. Therefore, the efficiency of cooling by natural circulation of the air conditioning refrigerant is improved, and the inside of the house 60 becomes comfortable.
  • the air in the house 60 is cooled and dehumidified only by heat-exchanging the air conditioning refrigerant with the atmosphere and naturally circulating the inside of the air conditioning refrigerant circuit 5. Is impossible.
  • the operation mode No. In 4-2 since the temperature of the hot water supply refrigerant flowing through the intermediate heat exchanger 23 can be arbitrarily adjusted by adjusting the opening degree of the hot water supply expansion valve 43, heat exchange is performed via the intermediate heat exchanger 23.
  • the temperature of the air conditioning refrigerant in the air conditioning refrigerant circuit 5 can be adjusted to a desired temperature (a temperature which is equal to or lower than the dew point temperature in the house 60). Therefore, even in the environment where the outside air temperature is equal to or higher than the dew point temperature in the house 60, the air in the house 60 can be cooled and dehumidified by the natural circulation cycle.
  • Operation mode No. 5 denotes an operation mode in which the cooling operation is performed by naturally circulating the air conditioning refrigerant in the air conditioning refrigerant circuit 5 using the outside air while performing the hot water supply operation by the hot water supply refrigerant circuit 6.
  • the air conditioning expansion valve 27 is adjusted to a predetermined opening degree in accordance with the amount of heat exchange desired to be obtained by the air conditioning use-side heat exchanger 28.
  • the air conditioning refrigerant accumulated in the air conditioning heat source side heat exchanger 24 dissipates heat to the outside air, condenses and liquefies.
  • the liquid refrigerant with a large density descends under the influence of gravity, passes through the expansion valve 27 for air conditioning, and flows through the air conditioning hot and cold water circulation circuit 8 while flowing through the air conditioning use heat exchanger 28 It absorbs heat and evaporates to gasify.
  • the evaporated refrigerant flows toward the heat source side heat exchanger 24 for air conditioning.
  • the air conditioning refrigerant circuit 5 is formed with a natural circulation cycle in which the air conditioning refrigerant naturally circulates.
  • the cold water radiated to the air conditioning refrigerant flowing through the air conditioning use-side heat exchanger 28 passes through the air conditioning cold and hot water piping by driving the air conditioning hot and cold water circulation pump 52 It flows into the exchanger 61.
  • the indoor heat exchanger 61 heat exchange is performed between the cold water in the air conditioning cold and hot water circulation circuit 8 and the high temperature air in the house 60, and the air of the house 60 is cooled. That is, the room of the house 60 is cooled. At this time, the cold water flowing through the indoor heat exchanger 61 absorbs heat from the air in the house 60 and is heated.
  • the heated cold water circulates in the air conditioning cold / hot water circulation circuit 8 by the air conditioning cold / hot water circulation pump 52 and exchanges heat with the air conditioning refrigerant circuit 5 while flowing through the air conditioning use side heat exchanger 28 again. , Is cooled to a predetermined temperature.
  • the gas refrigerant compressed by the hot water supply compressor 41 and brought to a high temperature and high pressure flows into the hot water supply use side heat exchanger 42.
  • the high-temperature, high-pressure gas refrigerant flowing in the hot water use side heat exchanger 42 dissipates heat to the water flowing in the hot water supply circuit 9, condenses and liquefies.
  • the supplied water becomes hot water of a predetermined temperature by receiving the heat from the hot water supply refrigerant circuit 6 by the hot water supply use side heat exchanger 42.
  • the liquefied high-pressure refrigerant is decompressed and expanded by the hot water supply expansion valve 43 to become a low temperature low pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant flows to the heat source side heat exchanger for hot water supply 44, absorbs heat from the atmosphere, evaporates, and becomes a low-pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the suction port 41a of the hot water supply compressor 41, is compressed again by the hot water supply compressor 41, and becomes a high temperature and high pressure gas refrigerant.
  • the control device 1a calculates results based on input signals such as a command signal from the remote control, detection signals of the temperature sensors TE1 to TE8, and a detection signal of the outside air temperature sensor. 1 to No. It is determined which of the selection conditions of the operation mode set in advance for each of the conditions 5 is satisfied, and the operation is controlled so as to select the operation mode according to the determination result.
  • set room temperature (Tr_st), set humidity (Hr_st), outside air temperature (Toa), cold water inlet temperature (Twbi), cold water outlet setting The temperature (Twb_st), the hot water supply output (Qhw), the water supply temperature (Twhi), and the hot water temperature (Twho) are used.
  • the set room temperature (Tr_st) is the room temperature set by the user using a remote control or the like.
  • the set humidity (Hr_st) is room humidity set by the user using a remote control or the like.
  • the outside air temperature (Toa) is the temperature of the outside air measured by the outdoor unit.
  • the cold water inlet temperature (Twbi) is a temperature measured by the cold / hot water system, and more specifically, a temperature measured by the temperature sensor TE1 of the cold / hot water circulation circuit 8 for air conditioning.
  • the chilled water outlet preset temperature (Twb_st) is a temperature determined by the control device 1a based on the preset room temperature (Tr_st), the preset humidity (Hr_st), and the chilled water inlet temperature (Twbi).
  • the hot water supply output (Qhw) is a value determined by the control device 1a from the user request and the water supply temperature (Twhi).
  • the water supply temperature (Twhi) is a temperature measured by the heat source hot water supply system, and more specifically, a temperature measured by the temperature sensor TE7.
  • the outlet hot water temperature (Twho) is a temperature determined based on the set value of the hot water use side outlet temperature (temperature measured by the temperature sensor TE8), the user's request, and the specification of the air conditioning and hot water supply system.
  • the control device 1a at predetermined timing, based on the input signal, (a) use side request, (b) water heater operation availability condition, (c) set room temperature Tr_st-function f1 (set room temperature Tr_st, set humidity Hr_st) And the difference between the outside air temperature Toa, (d) the difference between the set room temperature Tr_st-function f2 (Tr_st, Hr_st) and the outside air temperature Toa, (e) the difference between the cold water outlet set temperature Twb_st and the cold water inlet temperature Twbi, (f) compression Limit on machine operation time, (g) heat absorption-exhaust heat, ie, function f3 (Twb_st, Twbi, Toa) -function f4 (Qhw, Twhi, Twho, Toa) is determined. And according to the result of said (a)-(g), the control apparatus 1a is the driving
  • the control device 1a selects a suitable operation mode in accordance with the conditions. Moreover, when (a) is a "heating operation", the operation mode No. is unrelated to (b)-(g). Select 3 In FIG. 9, Time1, Time2, Time3, ⁇ T3, ⁇ T4, and ⁇ T6 are values determined in advance according to the specification of the air conditioning and hot water supply system.
  • the cooling load fluctuates from moment to moment, and the input difference is not 0 as the switching point (2 compressors-1 compressor), and the input difference> x1 (x1> 0).
  • Switching between the operation on the hot-water supply side only and the two-cycle compression type operation at the input difference ⁇ x2 (x2 ⁇ 0) can avoid frequent switching of the operation mode.
  • the fan of the air conditioning heat source side heat exchanger 24 is usually controlled to have a constant rotational speed.
  • the rotational speed control of the air conditioning compressor 21 is performed according to the outlet temperature of the air conditioning use-side heat exchanger 28 of the water circulating in the air conditioning cold / hot water circulation circuit 8 and the target temperature (in accordance with the indoor set temperature set by the user It is performed based on the deviation of the determined value).
  • the outlet temperature of the air-conditioning use side heat exchanger 28 for water is a value measured by the temperature sensor TE2 in the cooling operation, and is a value measured by the temperature sensor TE1 in the heating operation.
  • the controller 1a reduces the rotational speed of the air conditioning compressor 21 if "target temperature-outlet temperature> 0" in the cooling operation, and if "target temperature-outlet temperature ⁇ 0", the air conditioning compressor 21 Increase the speed of The control in the heating operation is also similar to the cooling operation, and if "target temperature-outlet temperature> 0", the rotational speed of the air conditioning compressor 21 is increased, and if "target temperature-outlet temperature ⁇ 0", The rotational speed of the air conditioning compressor 21 is reduced.
  • the control of the valve opening degree of the air conditioning expansion valve 27 is performed based on the suction temperature (the value measured by the temperature sensor TE3) of the air conditioning compressor 21, the number of rotations of the air conditioning compressor 21, and the heat absorption temperature. Specifically, the control device 1a is determined based on the number of rotations of the air conditioning compressor 21 and the heat absorption temperature so that the degree of superheat of the low pressure refrigerant gas at the suction of the air conditioning compressor 21 becomes a predetermined temperature. The amount of change of the expansion valve opening degree is determined from the deviation between the target value of suction temperature and the actual measurement value, and the air conditioning expansion valve 27 is operated to open (+ pulse) or close ( ⁇ pulse).
  • the “outside air temperature” is used in the heating operation as the heat sink temperature, and the inlet temperature of the use-side heat exchanger 28 for air conditioning of the cold water flowing in the cold water circulation circuit 8 for air conditioning
  • the measured temperature is used.
  • the target value of the suction temperature may be calculated using a predetermined function, or the suction temperature of the air conditioning compressor 21, the number of rotations of the air conditioning compressor 21, and the target values of the heat sink temperature and the suction temperature May be used in advance.
  • Control may be performed by the discharge temperature (the value measured by the temperature sensor TE4) instead of the suction temperature of the air conditioning compressor 21.
  • the control target is set for disturbance There is an advantage that the temperature is measured stably.
  • the fan of the heat source side heat exchanger 44 for hot water supply is usually controlled to have a constant rotational speed.
  • the hot water supply flow rate is controlled in accordance with the water supply temperature (the value measured by the temperature sensor TE7) of the water flowing through the hot water supply circuit 9 or a request from a hot water supply load side device (hot tub etc.) of the hot water supply circuit 9.
  • the number of revolutions of the hot water supply compressor 41 is controlled by the temperature of the water supplied to the hot water supply circuit 9 (the value measured by the temperature sensor TE8) and the hot water supplied to the bathtub (downstream of the hot water use side heat exchanger 42 This is performed according to the deviation from the target temperature (a value determined in consideration of the hot water supply set temperature set by the user) of the hot water flowing through Specifically, the controller 1a accelerates the rotational speed of the hot water supply compressor 41 if "target temperature-hot water supply temperature> 0" in hot water supply operation, and if "target temperature-hot water supply temperature ⁇ 0" The rotational speed of the hot water supply compressor 41 is reduced.
  • Control of the valve opening degree of the hot water supply expansion valve 43 is performed based on the suction temperature (a value measured by the temperature sensor TE5) of the hot water supply compressor 41, the number of rotations of the hot water supply compressor 41, and the heat source temperature. Specifically, the control device 1a is determined based on the number of rotations of the hot water supply compressor 41 and the heat absorption temperature so that the degree of superheat of the low pressure refrigerant gas at the suction of the hot water supply compressor 41 becomes a predetermined temperature. The amount of change of the expansion valve opening degree is determined from the deviation between the target value and the actual measurement value of the suction temperature, and the hot water supply expansion valve 43 is operated to open (+ pulse) or close ( ⁇ pulse).
  • the "outside air temperature” is used as the heat sink temperature.
  • the target value of the suction temperature may be calculated using a predetermined function, or the suction temperature of the hot water supply compressor 41, the number of rotations of the hot water supply compressor 41, and the target values of the heat sink temperature and the suction temperature. May be used in advance.
  • control may be performed by the discharge temperature (a value measured by the temperature sensor TE6) instead of the suction temperature of the hot water supply compressor 41.
  • the control target is set against disturbances There is an advantage that the temperature is measured stably.
  • the hot water supply flow rate is a target determined from the target values of the water supply temperature (the value measured by the temperature sensor TE7) flowing through the hot water supply circuit 9 and the hot water supply temperature (the temperature of hot water flowing downstream of the use side heat exchanger 42 for hot water supply) It is controlled according to the flow rate. Note that control may be performed to increase or decrease the hot water supply flow rate by comparing the water supply temperature and the target value of the hot water supply temperature.
  • the number of revolutions of the hot water supply compressor 41 is controlled by the outlet temperature of the hot water use side heat exchanger 42 in the hot water supply circuit 9, that is, the hot water outlet temperature (the value measured by the temperature sensor TE8) and the target temperature of hot water supply (use It is done according to the deviation from the request from the person and the value determined by the system specifications). Specifically, the control device 1a decelerates the number of revolutions of the hot water supply compressor 41 if "hot water supply target temperature-hot water supply outlet temperature ⁇ 0", and if "hot water supply target temperature-hot water supply outlet temperature> 0" The rotational speed of the hot water supply compressor 41 is increased. The rotational speed control of the hot water supply compressor 41 may be performed based on the water supply temperature and the target temperature of the hot water supply.
  • Control of the valve opening degree of the hot water supply expansion valve 43 is performed by using the suction temperature of the hot water supply compressor 41 (the value measured by the temperature sensor TE5) and the use side heat exchange of the water circulating in the air conditioning hot and cold water circulation circuit 8.
  • Target value of outlet temperature of outlet 28 (value measured by temperature sensor TE2) and inlet temperature of use-side heat exchanger 28 for air conditioning (value measured by temperature sensor TE1), and rotation speed of hot water supply compressor 41 It controls based on the target value of the valve-opening degree which becomes settled from these, and the actual value of a valve-opening degree.
  • the controller 1a opens the valve opening degree of the hot water supply expansion valve 43 (+ pulse) if "target value of valve opening degree-measured value of valve opening degree> 0", If the target value of the opening degree ⁇ the actual value of the valve opening degree ⁇ 0 ”, the valve opening degree of the hot water supply expansion valve 43 is closed ( ⁇ pulse).
  • a predetermined function may be used, or the suction temperature of the hot water supply compressor 41, the use of water circulating in the air conditioning cold / hot water circulation circuit 8 for air conditioning
  • the discharge temperature a value measured by the temperature sensor TE6
  • Control of the valve opening degree of the air conditioning expansion valve 27 is performed by using the target outlet temperature of the air conditioning use side heat exchanger 28 of the water circulating in the air conditioning cold and hot water circulation circuit 8 and the actually measured outlet temperature (measured by the temperature sensor TE2. Control based on the deviation of Specifically, if "target outlet temperature-measured outlet temperature ⁇ 0", the control device 1a opens the valve opening degree of the air conditioning expansion valve 27 (+ pulse), and "target outlet temperature-measured If the outlet temperature> 0 ”, the valve opening degree of the air conditioning expansion valve 27 is closed (-pulsed).
  • the hot water supply flow rate supplied from the hot water supply circuit 9 is the target outlet temperature of the air conditioning use side heat exchanger 28 of the water circulating in the cold and hot water circulation circuit 8 for air conditioning, and the actually measured inlet temperature (value measured by the temperature sensor TE1) Is controlled according to the deviation of Specifically, the controller 1a increases the hot water supply flow rate if "target inlet temperature-measured inlet temperature ⁇ 0", and if "target inlet temperature-measured inlet temperature>0", the hot water supply flow rate Reduce.
  • the number of revolutions of the hot water supply compressor 41 is controlled by the outlet temperature of the hot water use side heat exchanger 42 in the hot water supply circuit 9, that is, the hot water outlet temperature (the value measured by the temperature sensor TE8) and the target temperature of hot water supply (use It takes place according to the deviation from the value (determined in consideration of the hot water supply set temperature set by the user). Specifically, the control device 1a decelerates the number of revolutions of the hot water supply compressor 41 if "hot water supply target temperature-hot water supply outlet temperature ⁇ 0", and if "hot water supply target temperature-hot water supply outlet temperature> 0" The rotational speed of the hot water supply compressor 41 is increased. The rotational speed control of the hot water supply compressor 41 may be performed based on the water supply temperature and the target temperature of the hot water supply.
  • Control of the valve opening degree of the hot water supply expansion valve 43 is performed by using the suction temperature of the hot water supply compressor 41 (the value measured by the temperature sensor TE5) and the use side heat exchange of the water circulating in the air conditioning hot and cold water circulation circuit 8.
  • Target value of outlet temperature of outlet 28 (value measured by temperature sensor TE2) and inlet temperature of use-side heat exchanger 28 for air conditioning (value measured by temperature sensor TE1), and rotation speed of hot water supply compressor 41 It controls based on the target value of the valve-opening degree which becomes settled from these, and the actual value of a valve-opening degree.
  • the controller 1a opens the valve opening degree of the hot water supply expansion valve 43 (+ pulse) if "target value of valve opening degree-measured value of valve opening degree> 0", If the target value of the opening degree ⁇ the actual value of the valve opening degree ⁇ 0 ”, the valve opening degree of the hot water supply expansion valve 43 is closed ( ⁇ pulse).
  • a predetermined function may be used, or the suction temperature of the hot water supply compressor 41, the use of water circulating in the air conditioning cold / hot water circulation circuit 8 for air conditioning
  • the discharge temperature a value measured by the temperature sensor TE6
  • Control of the valve opening degree of the air conditioning expansion valve 27 is performed by using the target outlet temperature of the air conditioning use side heat exchanger 28 of the water circulating in the air conditioning cold and hot water circulation circuit 8 and the actually measured outlet temperature (measured by the temperature sensor TE2. Control based on the deviation of Specifically, if "target outlet temperature-measured outlet temperature ⁇ 0", the control device 1a opens the valve opening degree of the air conditioning expansion valve 27 (+ pulse), and "target outlet temperature-measured If the outlet temperature> 0 ”, the valve opening degree of the air conditioning expansion valve 27 is closed (-pulsed).
  • the control device 1a is a two-way valve upstream of the hot water supply heat source side heat exchanger 44 in the hot water supply refrigerant circuit 6. 49a is opened, and the fan of the heat source side heat exchanger 44 for hot water supply is operated.
  • the hot water supply refrigerant flowing through the hot water supply amount refrigerant circuit 6 can absorb heat from the outside air through the hot water supply heat source side heat exchanger 44. Therefore, the shortfall that could not be covered by the heat absorption from the natural circulation type cycle on the air conditioning side among the heat absorption required for the hot water supply cycle can be compensated by the heat absorption from the outside air.
  • the lack of heat absorption means the heat absorption estimated from the feed water temperature (temperature measured by the temperature sensor TE7) in the hot water supply circuit 9, the feed water flow rate or the rotational speed of the hot water supply compressor 41, and the air conditioning in the air conditioning cold and hot water circulation circuit 8. It can be judged by the difference between the chilled water inlet temperature (temperature measured by the temperature sensor TE1) of the usage side heat exchanger 28 and the required heat release estimated from the target value of the chilled water outlet temperature.
  • the control device 1a performs the two-way valve 35c before and after the air conditioning heat source side heat exchanger 24 in the air conditioning refrigerant circuit 5. , 35d to operate the fan of the heat source side heat exchanger 24 for air conditioning.
  • the air conditioning refrigerant that naturally circulates through the air conditioning refrigerant circuit 5 can dissipate heat to the outside air via the air conditioning heat source side heat exchanger 24. Therefore, it is possible to dissipate the remaining air conditioning exhaust heat to the hot water supply cycle among the air conditioning exhaust heat of the natural circulation type cycle, that is, the excess of the air conditioning exhaust heat to the outside air.
  • Excess heat removal means heat absorption estimated from the feed water temperature (temperature measured by the temperature sensor TE7) in the hot water supply circuit 9, the feed water flow rate or the rotational speed of the hot water supply compressor 41, and for air conditioning in the cold and hot water circulation circuit 8 for air conditioning. It can be determined by the difference between the chilled water inlet temperature (temperature measured by the temperature sensor TE1) of the use-side heat exchanger 28 and the required heat release estimated from the target value of the chilled water outlet temperature.
  • FIG. 10 (a) is a pressure-enthalpy diagram of the refrigerant of the air conditioning and hot water supply system according to the first embodiment of the present invention
  • FIG. 10 (b) is a pressure of the refrigerant of the conventional air conditioning and hot water supply system-enthalpy FIG.
  • the air conditioning refrigerant circuit 5 is operated at the compression type cycle at the time of cooling, and at the same time, the hot water supply refrigerant circuit 6 is operated at the compression type cycle.
  • the compression type cycle on the air conditioning side operates in the circulation path of PA1 ′ ⁇ PA2 ′ ⁇ PA3 ′ ⁇ PA4 ′
  • the compression type cycle on the hot water supply side is a circulation of PH1 ′ ⁇ PH2 ′ ⁇ PH3 ′ ⁇ PH4 ′ Work on the path.
  • PA 1 ′ is the state of the air conditioning refrigerant of the suction port 21 a of the air conditioning compressor 21
  • PA 2 ′ is the state of the air conditioning refrigerant of the discharge port 21 b of the air conditioning compressor 21
  • PA 3 ′ is the intermediate heat exchanger 23.
  • the state of the air conditioning refrigerant at the outlet, PA 4 ′ is the state of the air conditioning refrigerant at the inlet of the air conditioning use-side heat exchanger 28.
  • PH1 ' is the state of the hot water supply refrigerant of the suction port 41a of the hot water supply compressor 41
  • PH2' is the state of the hot water supply refrigerant of the discharge port 41b of the hot water supply compressor 41
  • PH3 ' is the use side heat exchanger for hot water supply
  • PH4 ' is the state of the hot water supply refrigerant at the inlet of the intermediate heat exchanger 23.
  • the air conditioning refrigerant circuit 5 is operated in the natural circulation type cycle at the time of cooling, and at the same time the hot water supply refrigerant circuit 6 is operated in the compression type cycle (e.g. 4-2), as shown in FIG. 10A, the natural circulation type cycle on the air conditioning side operates in the circulation path of PA1 ⁇ PA2 ⁇ PA3, and the compression type cycle on the hot water supply side is PH1 ⁇ PH2 ⁇ Operates in the circulation path PH3 ⁇ PH4.
  • PA1 is the state of the air conditioning refrigerant at the outlet of the intermediate heat exchanger 23
  • PA2 is the state of the air conditioning refrigerant at the inlet of the use side exchanger 28
  • PA3 is the air conditioning refrigerant at the inlet of the intermediate heat exchanger 23.
  • PH1 is the state of the hot water supply refrigerant of the suction port 41a of the hot water supply compressor 41
  • PH2 is the state of the hot water supply refrigerant of the discharge port 41b of the hot water supply compressor 41
  • PH3 is the outlet of the hot water use side heat exchanger 42
  • the state of the hot water supply refrigerant, PH4 is the state of the hot water supply refrigerant at the inlet of the intermediate heat exchanger 23.
  • the operation mode is a combination of the natural circulation type cycle on the air-conditioning side and the hot-water supply cycle to improve the operation efficiency and contribute to energy saving. A significant reduction can be realized.
  • an air conditioning and hot water supply system according to a second embodiment of the present invention will be described with reference to FIG. 11.
  • the same reference numerals are given to the same components as those of the air conditioning and hot water supply system according to the first embodiment. The explanation is omitted.
  • the air conditioning and hot water supply system according to the second embodiment is different from the air conditioning and hot water supply system according to the first embodiment in that a heat storage and hot water storage unit 7 is provided in the hot water supply circuit 9. This difference will be described in detail below.
  • the heat storage and hot water storage unit 7 is configured to include a hot water storage tank 70 and a heat storage tank 71.
  • the hot water storage tank 70 and the heat storage tank 71 use hot water supply pipes 72 and 73 constituting the hot water supply circuit 9 and pipes respectively. Is connected.
  • the hot water storage tank 70 is a tank capable of storing heat and storing hot water generated by heat exchange with the hot water supply refrigerant circuit 6.
  • the heat storage tank 71 is a tank capable of storing heat, and the heat collected by the solar heat collector 74 is taken in. The water in the heat storage tank 71 is warmed by the solar heat collector 74 to a temperature (intermediate temperature) between cold water and hot water.
  • the water in the hot water supply circuit 9 flows in the direction of the arrow in FIG. 9 by driving the hot water supply circulation pump, and exchanges heat with the hot water supply refrigerant in the hot water use utilization side heat exchanger 42 to become hot water. , Flows to the storage tank 70.
  • the pipe for supplying hot water from the hot water storage tank 70 to the device on the hot water supply load side and the pipe for supplying water at an intermediate temperature from the heat storage tank 50 to the bathtub on the hot water supply load side are merged in the heat storage and hot water storage unit 7
  • a three-way valve (not shown) is provided at the junction of the pipe and the pipe.
  • the hot water supply pump which is not shown in figure is provided in the piping connected to the apparatus by the side of a hot water supply load.
  • the air conditioning (cooling) load occurs in the daytime to the evening in a general house, the hot water supply demand exists at night. That is, it is general that there is a difference (a gap) between the time zone in which the cooling operation is mainly performed and the time zone in which the hot water supply operation is mainly performed.
  • a gap between the time zone in which the cooling operation is mainly performed and the time zone in which the hot water supply operation is mainly performed.
  • the hot water supply circuit 9 and a device (such as a bathtub) on the hot water supply load side are directly connected, during the night time zone where hot water supply demand occurs. Only the operation in the operation mode (operation mode No. 4-1, No. 4-2) using the hot water supply cycle and the natural circulation cycle on the air conditioning side can be performed.
  • the air conditioning and hot water supply system since the heat storage and storage unit 7 is provided, the hot water stored in the heat storage tank 50 and the hot water storage tank 70 can be supplied at any time. Can. Explaining in a little more detail, in the second embodiment, even when there is no hot water supply load, while performing air conditioning by the natural circulation type cycle while operating the hot water supply cycle, the hot water obtained by the hot water supply operation is stored. By storing in the hot water storage unit 7, hot water can be used when necessary. Therefore, the air conditioning and hot water supply system according to the second embodiment can easily utilize the operation mode based on the natural circulation type cycle, and the power consumption of the air conditioning and hot water supply system can be reduced.
  • the solar heat collector 74 may be incorporated into the hot water storage tank 70.
  • the water of the heat storage tank 71 is introduced to the intermediate heat exchanger 23, and in this intermediate heat exchanger 23, the air conditioning refrigerant of the air conditioning refrigerant circuit 5 and the hot water supply refrigerant of the hot water supply refrigerant circuit 6 Heat exchange may be performed between the three fluids with the water (intermediate temperature water). According to this configuration, the exhaust heat from the cooling operation can be used more effectively, and the energy saving effect is also enhanced.
  • an air conditioning and hot water supply system according to a third embodiment of the present invention will be described with reference to FIG. 12.
  • the same reference numerals are used for the same components as those of the air conditioning and hot water supply system according to the first embodiment. The explanation is omitted.
  • two of the first air conditioning use side split heat exchanger 28 a and the second air conditioning use side split heat exchanger 28 b as the air conditioning use side heat exchangers are two of the first air conditioning use side split heat exchanger 28 a and the second air conditioning use side split heat exchanger 28 b as the air conditioning use side heat exchangers.
  • the first air conditioning use side split heat exchanger 28a and the second air conditioning use side split heat exchanger 28b both flow through the air conditioning refrigerant flowing through the air conditioning refrigerant circuit 5 and the air conditioning cold water / hot water circulation circuit 8
  • the heat exchange with water is possible, and the first air conditioning use side split heat exchanger 28 a and the second air conditioning use side split heat exchanger 28 b are connected in series.
  • the first air conditioning user-side split heat exchanger 28a and the second air-conditioning user-side split heat exchanger 28b are installed at a lower position than the air-conditioning heat source side heat exchanger 24 in order to provide a head difference. It is done.
  • the branch point E to be connected is connected by the second air conditioning refrigerant bypass pipe 29b.
  • An air conditioning auxiliary expansion valve 27 b is incorporated in the second air conditioning refrigerant bypass pipe 29 b.
  • the third air conditioning refrigerant bypass pipe 29 c is connected to a branch point F located between the two.
  • a two-way valve 35f is incorporated in the air conditioning refrigerant bypass pipe 29b. Furthermore, between the branch point E and the branch point F, a two-way valve 35g is provided.
  • the first natural circulation path is a path that follows a branch point B ⁇ a branch point I ⁇ a branch point D ⁇ a branch point E ⁇ a branch point A ⁇ a branch point B.
  • the air conditioning refrigerant that has been liquefied by exchanging heat with the hot water supply refrigerant flowing in the hot water supply refrigerant circuit 6 by the intermediate heat exchanger 23 naturally condenses the air conditioning refrigerant bypass piping 29b due to the density difference.
  • the liquefied air conditioning refrigerant absorbs heat from the water flowing in the air conditioning cold and hot water circulation circuit 8 by the second air conditioning use side split heat exchanger 28b and evaporates, and naturally passes through the air conditioning refrigerant bypass pipe 29 , Return to the intermediate heat exchanger 23.
  • the two-way valve 35b, the two-way valve 35c, and the two-way valve 35f are closed, and the air conditioning auxiliary expansion valve 27b has an appropriate valve opening degree. It has been adjusted.
  • the second natural circulation route is a route which follows a branch point B ⁇ branch point I ⁇ branch point D ⁇ branch point J ⁇ branch point F ⁇ branch point E ⁇ branch point A ⁇ branch point B.
  • the air conditioning refrigerant that has been liquefied by exchanging heat with the hot water supply refrigerant flowing in the hot water supply refrigerant circuit 6 in the intermediate heat exchanger 23 is naturally transferred to the air conditioning refrigerant tank 26 due to the density difference. It flows and flows through the air conditioning expansion valve 27 in the order of the first air conditioning use side heat exchanger 28 a and the second air conditioning use side divided heat exchanger 28 b.
  • the liquefied air conditioning refrigerant While flowing through the first air conditioning use-side heat exchanger 28a and the second air conditioning use-side divided heat exchanger 28b in order, the liquefied air conditioning refrigerant is circulated from the water flowing in the air conditioning cold / hot water circulation circuit 8 It absorbs heat, evaporates, and naturally returns to the intermediate heat exchanger 23 through the air conditioning refrigerant bypass pipe 29.
  • the two-way valve 35c, the two-way valve 35d, the two-way valve 35f, and the air conditioning auxiliary expansion valve 27b are closed, and the air conditioning expansion valve 27 is , Has been adjusted to an appropriate degree of valve opening.
  • the third natural circulation route is a route that follows a branch point B ⁇ a branch point I ⁇ a branch point C ⁇ a branch point J ⁇ a branch point F ⁇ a branch point E ⁇ a branch point A ⁇ a branch point B.
  • the air conditioning refrigerant that has been liquefied by exchanging heat with the air in the air conditioning heat source side heat exchanger 24 flows naturally to the air conditioning refrigerant tank 26 due to the density difference, and the air conditioning expansion
  • the first air-conditioning use side heat exchanger 28 a and the second air-conditioning use side divided heat exchanger 28 b flow in this order via the valve 27.
  • the liquefied air conditioning refrigerant absorbs heat from the water flowing in the air conditioning cold and hot water circulation circuit 8 by the first air conditioning use side heat exchanger 28a and the second air conditioning use side split heat exchanger 28b and evaporates.
  • the air conditioning refrigerant bypass piping 29 naturally returns to the heat source side heat exchanger 24 for air conditioning.
  • the fourth natural circulation route is a route which follows a branch point C ⁇ a branch point J ⁇ a branch point F ⁇ a branch point C.
  • the air conditioning refrigerant that has been liquefied by exchanging heat with the air in the heat source side heat exchanger 24 for air conditioning flows naturally to the air conditioning refrigerant tank 26 due to the density difference, and the expansion for air conditioning It flows to the first air conditioning use side heat exchanger 28 a via the valve 27.
  • the liquefied air conditioning refrigerant absorbs heat from the water flowing in the air conditioning cold and hot water circulation circuit 8 by the first air conditioning use side heat exchanger 28a and evaporates, and naturally the third air conditioning refrigerant bypass pipe 29c It passes through and returns to the heat source side heat exchanger 24 for air conditioning.
  • the third natural circulation path is formed, the two-way valve 35a, the two-way valve 35b, the two-way valve 35c, the two-way valve 35e, and the air conditioning auxiliary expansion valve 27b are closed.
  • the expansion valve 27 is adjusted to an appropriate valve opening degree.
  • the indoor temperature of the house 60 and The control device 1a can select an optimal natural circulation type cycle considering the relationship with the outdoor temperature, the indoor dew point temperature, and other environmental conditions. Therefore, since the variation of utilization of a natural circulation cycle increases and the case where the operation which stopped the air-conditioning compressor 21 can be performed increases, the air-conditioning and hot-water supply system concerning the 3rd example of an embodiment consumes electric power concerning operation of an air-conditioning cycle. Can be reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention concerne un système de climatisation et de fourniture d'eau chaude qui permet le refroidissement et la déshumidification par un cycle de circulation naturel même si la température extérieure correspond au moins au point de rosée à l'intérieur. Le système de climatisation et de fourniture d'eau chaude comprend : un trajet de réfrigérant de climatiseur (5) ; un trajet de réfrigérant de fourniture d'eau chaude (6) qui fournit de l'eau chaude ; et un échangeur de chaleur intermédiaire (6) qui échange de la chaleur entre le trajet de réfrigérant de climatiseur et le trajet de réfrigérant de fourniture d'eau chaude. Le trajet de réfrigérant de climatiseur est formé à la manière d'une boucle en reliant séquentiellement à des conduites de réfrigérant un compresseur de climatiseur (21), une soupape de commutation de canalisation de climatiseur (22), l'échangeur de chaleur intermédiaire (23), une soupape de détente de climatiseur (27), et un échangeur de chaleur de côté d'utilisation de climatiseur (28). Le trajet de réfrigérant de fourniture d'eau chaude est formé à la manière d'une boucle en reliant séquentiellement à des conduites de réfrigérant un compresseur de fourniture d'eau chaude (41), un échangeur de chaleur de côté d'utilisation de fourniture d'eau chaude (42), une soupape de détente de fourniture d'eau chaude (43), et l'échangeur de chaleur intermédiaire (23). Ensuite, un moyen d'ouverture/de fermeture de dérivation (34a, 34b) et des tuyaux de dérivation (29) qui contournent le compresseur de climatiseur sont disposés dans le trajet de réfrigérant de climatiseur. L'échangeur de chaleur intermédiaire est disposé au niveau d'une position qui est supérieure à celle de l'échangeur de chaleur de côté d'utilisation de climatiseur.
PCT/JP2010/053275 2010-03-01 2010-03-01 Système de climatisation et de fourniture d'eau chaude Ceased WO2011108068A1 (fr)

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CN201080064512.4A CN102770725B (zh) 2010-03-01 2010-03-01 空气调节热水供给系统
PCT/JP2010/053275 WO2011108068A1 (fr) 2010-03-01 2010-03-01 Système de climatisation et de fourniture d'eau chaude
JP2012502911A JP5373964B2 (ja) 2010-03-01 2010-03-01 空調給湯システム

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JP2013103632A (ja) * 2011-11-15 2013-05-30 Furukawa Electric Co Ltd:The 自動車用の暖房システム、熱輸送システム
JP2013113533A (ja) * 2011-11-30 2013-06-10 Hitachi Appliances Inc 空気調和機および空気調和機の運転方法
WO2013128668A1 (fr) 2012-03-02 2013-09-06 株式会社 日立製作所 Système de récupération de chaleur des gaz d'échappement et procédé de fonctionnement pour celui-ci
JPWO2013061473A1 (ja) * 2011-10-28 2015-04-02 株式会社日立製作所 給湯空調装置
JPWO2013080297A1 (ja) * 2011-11-29 2015-04-27 株式会社日立製作所 空調給湯システム
WO2015081997A1 (fr) * 2013-12-04 2015-06-11 Electrolux Appliances Aktiebolag Système de réfrigération
CN109974318A (zh) * 2017-12-27 2019-07-05 杭州三花研究院有限公司 一种热管理系统
JP7019215B1 (ja) 2020-09-11 2022-02-15 オリオン機械株式会社 冷温同時温度調整装置
JP7019213B1 (ja) 2020-09-11 2022-02-15 オリオン機械株式会社 冷温同時温度調整装置
JP7019211B1 (ja) 2020-09-11 2022-02-15 オリオン機械株式会社 冷温同時温度調整装置
EP4328527A4 (fr) * 2021-04-22 2024-05-29 Mitsubishi Electric Corporation Chauffe-eau à pompe à chaleur

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CN109253486B (zh) * 2018-09-29 2020-10-09 杨晓军 一种自然循环和强制循环在同一供热系统中的混装构造
CN109405102B (zh) * 2018-10-08 2024-01-16 珠海格力电器股份有限公司 空调系统

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JPH05204466A (ja) * 1991-07-05 1993-08-13 Takenaka Komuten Co Ltd 流量制御弁の制御方法
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JPWO2013061473A1 (ja) * 2011-10-28 2015-04-02 株式会社日立製作所 給湯空調装置
JP2013103632A (ja) * 2011-11-15 2013-05-30 Furukawa Electric Co Ltd:The 自動車用の暖房システム、熱輸送システム
JPWO2013080297A1 (ja) * 2011-11-29 2015-04-27 株式会社日立製作所 空調給湯システム
JP2013113533A (ja) * 2011-11-30 2013-06-10 Hitachi Appliances Inc 空気調和機および空気調和機の運転方法
WO2013128668A1 (fr) 2012-03-02 2013-09-06 株式会社 日立製作所 Système de récupération de chaleur des gaz d'échappement et procédé de fonctionnement pour celui-ci
WO2015081997A1 (fr) * 2013-12-04 2015-06-11 Electrolux Appliances Aktiebolag Système de réfrigération
CN109974318A (zh) * 2017-12-27 2019-07-05 杭州三花研究院有限公司 一种热管理系统
JP7019215B1 (ja) 2020-09-11 2022-02-15 オリオン機械株式会社 冷温同時温度調整装置
JP7019213B1 (ja) 2020-09-11 2022-02-15 オリオン機械株式会社 冷温同時温度調整装置
JP7019211B1 (ja) 2020-09-11 2022-02-15 オリオン機械株式会社 冷温同時温度調整装置
JP2022046850A (ja) * 2020-09-11 2022-03-24 オリオン機械株式会社 冷温同時温度調整装置
JP2022046848A (ja) * 2020-09-11 2022-03-24 オリオン機械株式会社 冷温同時温度調整装置
JP2022046846A (ja) * 2020-09-11 2022-03-24 オリオン機械株式会社 冷温同時温度調整装置
EP4328527A4 (fr) * 2021-04-22 2024-05-29 Mitsubishi Electric Corporation Chauffe-eau à pompe à chaleur

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