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WO2011108068A1 - Air-conditioning hot-water-supplying system - Google Patents

Air-conditioning hot-water-supplying system 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
Authority
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
Other languages
French (fr)
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 JP2012502911A priority Critical patent/JP5373964B2/en
Priority to PCT/JP2010/053275 priority patent/WO2011108068A1/en
Priority to CN201080064512.4A priority patent/CN102770725B/en
Publication of WO2011108068A1 publication Critical patent/WO2011108068A1/en
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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Abstract

Disclosed is an air-conditioning hot-water-supplying system that enables cooling and dehumidification by a natural circulation cycle even if the outside temperature is at least the indoor dew point. The air-conditioning hot-water-supplying system is provided with: an air-conditioner refrigerant pathway (5); a hot-water-supply refrigerant pathway (6) that supplies hot water; and an intermediate heat exchanger (23) that exchanges heat between the air-conditioner refrigerant pathway and the hot-water-supply refrigerant pathway. The air-conditioner refrigerant pathway is formed in a loop by sequentially connecting with refrigerant pipes an air-conditioner compressor (21), an air-conditioner duct-switching valve (22), the intermediate heat exchanger (23), an air-conditioner expansion valve (27), and an air-conditioner use-side heat exchanger (28). The hot-water-supply refrigerant pathway is formed in a loop by sequentially connecting with refrigerant pipes a hot-water-supply compressor (41), a hot-water-supply use-side heat exchanger (42), a hot-water-supply expansion valve (43), and the intermediate heat exchanger (23). Then, bypass opening/closing means (34a, 34b) and bypass tubing (29) that bypasses the air-conditioner compressor are provided to the air-conditioner refrigerant pathway. The intermediate heat exchanger is disposed at a position that is higher than that of the air-conditioner use-side heat exchanger.

Description

空調給湯システムAir conditioning hot water system

　本発明は、冷房と暖房とを切替えて行う空調用冷媒回路と給湯を行う給湯用冷媒回路とを中間熱交換器を介して互いに熱交換可能に接続して、空調用冷凍サイクルと給湯用冷凍サイクルの二元冷凍サイクルが形成される空調給湯システムに係り、特に、空調用冷凍サイクルとして、空調用冷媒が密度差により自然循環する自然循環式サイクルと、空調用圧縮機により空調用冷媒が強制循環する圧縮式サイクルの２つの空調用冷凍サイクルを使い分けることが可能な空調給湯システムに関する。 According to the present invention, 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. In particular, as a refrigeration cycle for air conditioning, 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.

　自然循環式サイクルと圧縮式サイクルとの２つの冷凍サイクルを使い分ける従来技術として、例えば、特許文献１には、室内熱交換器と、室外熱交換器と、冷媒配管と、膨張弁と、別装置の圧縮冷凍機に相当する冷媒圧縮強制循環装置とを備えた冷媒自然循環冷却除湿装置が開示されている。この冷媒自然循環冷却除湿装置は、室外熱交換器と、この室外熱交換器より低い位置にある室内熱交換器と、膨張弁とを冷媒配管で環状に接続して形成された自然循環式サイクルと、冷媒圧縮強制循環装置による圧縮式サイクルとを有しており、自然循環式サイクルの室外熱交換器に対して圧縮式サイクルの蒸発熱交換器が密結合した構成となっている。この構成によれば、蒸発熱交換器は、室外熱交換器から熱を効率的に奪うことができるため、室内と室外との気温差が無くなり冷却除湿能力が低下したような場合であっても、冷媒圧縮強制循環装置を稼働することにより、冷媒自然循環冷却除湿装置の冷却除湿能力の低下を補うことができる。 For example, 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. And 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.

特開平１０－３００１２８号公報Japanese Patent Application Laid-Open No. 10-300128

　しかしながら、上記従来の技術では、自然循環式サイクルと圧縮式サイクルとが独立した冷凍サイクルを構成しているので、自然循環式サイクルの熱交換器を、冷暖房のピーク時などに圧縮式サイクルの熱交換器として利用することは不可能であった。そのため、自然循環式サイクルの熱交換器の熱交換機能が有効に活用されていないといった課題があった。また、上記従来の技術では、外気温度が室内温度以上の場合に、室内から外気への放熱を圧縮式サイクルで行っており、その放熱を有効に活用していないといった課題があった。また、外気温度が室内の露点温度以上である場合には、自然循環式サイクルのみで冷却除湿を行うことができないといった課題があった。 However, in the above-mentioned conventional technology, since the natural circulation type cycle and the compression type cycle constitute an independent refrigeration cycle, 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.

　本発明は、上記した実情に鑑みてなされたものであり、その第１の目的は、自然循環式サイクルの熱交換器を圧縮式サイクルの熱交換器として利用することができる空調給湯システムを提供することにある。また、本発明の第２の目的は、圧縮式サイクルからの放熱を有効に活用できる空調給湯システムを提供することにある。また、本発明の第３の目的は、外気温度が室内の露点温度以上である場合であっても、自然循環式サイクルによる冷却除湿を可能とする空調給湯システムを提供することにある。 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.

　上記目的を達成するために、本発明に係る空調給湯システムは、冷房運転と暖房運転とを切替えて行う空調用冷媒回路と、給湯を行う給湯用冷媒回路と、前記空調用冷媒回路を循環する空調用冷媒と前記給湯用冷媒回路を循環する給湯用冷媒との間で熱交換を行う中間熱交換器とを備えた空調給湯システムであって、前記空調用冷媒回路を、空調用圧縮機、空調用流路切替弁、前記中間熱交換器、空調用膨張弁、空調用利用側の熱搬送媒体（例えば、室内空気、水、またはブライン）と熱交換を行うための空調用利用側熱交換器を順次冷媒配管で接続して環状に形成し、前記給湯用冷媒回路を、給湯用圧縮機、給湯用利用側の熱搬送媒体（例えば、水）と熱交換を行う給湯用利用側熱交換器、給湯用膨張弁、前記中間熱交換器を順次冷媒配管で接続して環状に形成し、前記空調用冷媒回路に、前記空調用圧縮機をバイパスするバイパス配管と、前記空調用冷媒の流路を、前記空調用圧縮機を経由する流路と前記バイパス配管を経由する流路との何れかに切り替えるバイパス開閉手段とを設け、前記中間熱交換器を前記空調用利用側熱交換器より高い位置に設置したことを特徴とするものである。 In order to achieve the above object, an air conditioning and hot water supply system according to the present invention 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.

　本発明によれば、空調用圧縮機を用いて空調用冷媒を空調用冷媒回路内で強制循環させるようにした圧縮式サイクルによる運転ができるうえ、中間熱交換器と空調用利用側熱交換器との間にヘッド差があるため、空調用圧縮機をバイパスするバイパス配管を用いて、空調用冷媒の密度差を利用した自然循環式サイクルによる運転を行うことができる。つまり、１つの空調用冷媒回路で、圧縮式サイクルと自然循環式サイクルの両方のサイクルを構成することができる。よって、本発明は、自然循環式サイクルの熱交換器を圧縮式サイクルの熱交換器として有効利用することができる。また、本発明は、圧縮式サイクルと自然循環式サイクルとを利用環境に応じて適宜切り替えて運転することにより、消費電力を低減することができる。特に、本発明は、冷房負荷が小さいため空調用圧縮機を断続的に運転するような場合には、自然循環式サイクルによる運転を行うことにより、消費電力を大幅に低減することができるのである。 According to 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. In other words, one air conditioning refrigerant circuit can constitute both a compression type cycle and a natural circulation type cycle. Thus, the present invention can effectively utilize the natural circulation cycle heat exchanger as a compression cycle heat exchanger. Further, according to the present invention, power consumption can be reduced by appropriately switching and operating the compression cycle and the natural circulation cycle according to the usage environment. In particular, according to the present invention, when the air conditioning compressor is operated intermittently because the cooling load is small, the power consumption can be significantly reduced by operating the natural circulation type cycle. .

　さらに、本発明では、中間熱交換器により、空調用冷媒回路を流れる空調用冷媒と給湯用冷媒回路を流れる給湯用冷媒との間で熱交換を行うことが可能であるため、空調用冷媒回路の自然循環式サイクルにおいて、中間熱交換器を凝縮器として用いることができる。つまり、中間熱交換器内にある空調用冷媒を、中間熱交換器に流入する低温の給湯用冷媒へ放熱させることにより、その空調用冷媒を凝縮して液化させることができる。よって、本発明は、温度差が小さくても自然循環式サイクルにより大きな冷却能力を確保することができる。 Furthermore, in the present invention, 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.

　ここで、外気温度と室内温度との差が小さい場合には、外気を放熱源とした自然循環式サイクルでは、冷却能力を大きくすることはできないが、本発明では、中間熱交換器によって給湯用冷媒と空調用冷媒との熱交換を行うことができるため、外気温度と室内温度との差が小さい場合でも、確実に自然循環式サイクルを運転することができる。つまり、給湯用冷媒回路を流れる給湯用冷媒の吸熱作用によって、自然循環式サイクルの動作をアシストすることができるのである。 Here, when the difference between the outside air temperature and the room temperature 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.

　また、外気温度が室内空気の露点温度以上の場合には、自然循環式サイクルのみによる運転では室内空気の冷却除湿を行うことはできないが、本発明では、給湯用冷媒回路に組み込まれた給湯用膨張弁の弁開度を適宜調整することにより給湯用冷媒の温度を調整できるため、空調用冷媒の温度を中間熱交換器を介して任意の温度に下げることができる。よって、本発明は、外気温度が室内空気の露点温度以上の場合であっても、室内を冷却除湿することができる。 Further, when 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. However, in the present invention, for hot water supply incorporated in the hot water supply refrigerant circuit. Since 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.

　また、本発明に係る空調給湯システムは、上記構成において、前記空調用冷媒回路に、空調用熱源側の熱搬送媒体（例えば、大気）と前記空調用冷媒との間で熱交換するための空調用熱源側熱交換器を前記中間熱交換器と並列にして設け、前記給湯用冷媒回路に、給湯用熱源側の熱搬送媒体（例えば、大気）と前記給湯用冷媒との間で熱交換するための給湯用熱源側熱交換器を前記中間熱交換器と並列にして設け、前記空調用熱源側熱交換器を前記空調用利用側熱交換器よりも高い位置に設置したことを特徴としている。 In the air-conditioning and hot-water supply system according to the present invention, in the above-described configuration, 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 .

　本発明によれば、空調用冷媒回路と給湯用冷媒回路をそれぞれ単独で運転することもできる。加えて、本発明は、空調用熱源側熱交換器と空調用利用側熱交換器との間にヘッド差が設けられているため、給湯用冷媒回路による給湯サイクルの運転を行わなくても、空調用熱源側熱交換器と空調用利用側熱交換器との間で空調用冷媒を自然循環させることもできる。よって、本発明は、消費電力の低減効果を高めることができる。 According to the present invention, the air conditioning refrigerant circuit and the hot water supply refrigerant circuit can each be operated independently. In addition, according to the present invention, since the head difference is provided between the heat source side heat exchanger for air conditioning and the use side heat exchanger for air conditioning, 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.

　また、本発明に係る空調給湯システムは、上記構成において、前記空調用利用側熱交換器と被空調空間（例えば、住宅）に設置された室内熱交換器との間を配管で接続して空調用熱搬送媒体循環回路を形成し、前記空調用熱搬送媒体循環回路に前記空調用利用側の熱搬送媒体としての水またはブラインを循環させるようにしたことを特徴としている。 In the air-conditioning and hot-water supply system according to the present invention, in the above configuration, the air-conditioning use-side heat exchanger and an indoor heat exchanger installed in an air-conditioned space (for example, a house) 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.

　本発明によれば、従来のように室内機と室外機をつなぐ冷媒配管が不要となるうえ、冷媒量が少なくて済む。また、従来のような室内機と室外機とを冷媒配管で接続する構成において自然循環式サイクルを形成する場合には、室外機を室内機よりも高い位置に設置する必要があり、レイアウトの制約があった。ところが、本発明によれば、空調用熱搬送媒体循環回路を設ける構成であるため、レイアウトの自由度が増すという利点がある。 According to the present invention, 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. In addition, when 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. However, according to the present invention, since the heat transfer medium circulation circuit for air conditioning is provided, there is an advantage that the degree of freedom in layout is increased.

　また、本発明に係る空調給湯システムは、上記構成において、前記給湯用利用側熱交換器の入口と出口に、前記給湯用利用側の熱搬送媒体としての水が流れる配管をそれぞれ接続して給湯回路を形成し、前記給湯回路に、水が前記給湯用利用側熱交換器から得た熱を蓄えることが可能なタンク（例えば、貯湯タンク、蓄熱タンクと称されるタンク）を設けたことを特徴としている。 Further, in the air conditioning and hot water supply system according to the present invention, in the above configuration, 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.

　本発明によれば、空調排熱を回収して給湯用利用側熱交換器から得た温熱をタンクに蓄えることができるため、熱エネルギの有効利用が図られ、エネルギ効率が高まる利点がある。また、本発明は、タンクに蓄熱することができるため、空調負荷と給湯負荷の時間帯の相違を解消することも可能である。例えば、本発明では、冷房負荷はあるものの給湯負荷がない昼間に給湯サイクルを運転しながら被冷却空間を自然循環式サイクルによる冷房を行い、その給湯サイクルの運転中に得た温熱をタンクに蓄熱することができる。分かり易く言えば、本発明は、昼間に冷房しながらお湯を沸かし、そのお湯を夜間に利用することができるのである。 According to 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. For example, according to the present invention, 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. To put it plainly, the present invention can boil hot water while cooling in the daytime, and can use the hot water at night.

　また、本発明に係る空調給湯システムは、上記構成において、前記空調用冷媒回路および前記給湯用冷媒回路の運転を制御する制御装置を備え、前記制御装置は、利用者によって設定される設定室温(Tr_st)と、利用者によって設定される設定湿度(Hr_st)と、外気温度(Toa)と、前記空調用利用側の熱搬送媒体の前記空調用利用側熱交換器入口の温度(Twbi)と、前記設定室温、前記設定湿度および前記空調用利用側の熱搬送媒体の前記空調用利用側熱交換器入口の温度に基づいて決定される前記空調用利用側の熱搬送媒体の前記空調用利用側熱交換器出口の設定温度(Twb_st)と、前記給湯用利用側の熱搬送媒体の前記給湯用利用側熱交換器入口の温度(Twhi)と、利用者の要求および前記給湯用利用側の熱搬送媒体の前記給湯用利用側熱交換器入口の温度に基づいて決定される給湯出力(Qhw)と、前記給湯用利用側の熱搬送媒体の前記給湯用利用側熱交換器出口の出湯温度(Twho)とに基づいて、複数の運転モードの中から何れかを選択することを特徴としている。 In the air conditioning and hot water supply system according to the present invention, in the above configuration, 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 supply medium One of a plurality of operation modes based on the hot water supply output (Qhw) determined based on the hot water supply use outlet side heat exchanger outlet of the hot water supply use side heat transfer medium determined based on It is characterized by selecting.

　本発明によれば、制御装置によって好適な運転モードを選択できるため、快適な室内空間を維持できるうえ、省エネ性が向上する。 According to the present invention, since a suitable operation mode can be selected by the control device, a comfortable indoor space can be maintained, and energy saving can be improved.

　本発明によれば、冷房負荷が小さく圧縮機が断続運転をするような場合で、給湯機を動かす必要がある場合（中間期）に、空調用サイクルの圧縮機を運転することなく、給湯サイクルの膨張弁開度により、蒸発温度を下げることで任意の温度（除湿可能な温度）レベルの冷水を作ることができる。これにより空調サイクルを効率の悪い領域で運転することなく冷房運転が可能となり、消費電力を低減できる。 According to the present invention, when the cooling load is small and the compressor is operated intermittently and the hot water heater needs to be operated (intermediate period), 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.

本発明の第１の実施の形態例に係る空調給湯システムの系統図である。BRIEF DESCRIPTION OF THE DRAWINGS It is a systematic diagram of the air-conditioning and hot water supply system which concerns on the example of the 1st Embodiment of this invention. 図１に示す空調給湯システムの運転モードＮｏ．１における冷媒と熱搬送媒体の流れを示す動作図である。Operation mode No. of the air conditioning and hot water supply system shown in FIG. FIG. 6 is an operation diagram showing flows of the refrigerant and the heat transfer medium in 1; 図１に示す空調給湯システムの運転モードＮｏ．２－１における冷媒と熱搬送媒体の流れを示す動作図である。Operation mode No. of the air conditioning and hot water supply system shown in FIG. FIG. 7 is an operation diagram showing flows of a refrigerant and a heat transfer medium in 2-1. 図１に示す空調給湯システムの運転モードＮｏ．２－２における冷媒と熱搬送媒体の流れを示す動作図である。Operation mode No. of the air conditioning and hot water supply system shown in FIG. FIG. 8 is an operation diagram showing flows of a refrigerant and a heat transfer medium in 2-2. 図１に示す空調給湯システムの運転モードＮｏ．３における冷媒と熱搬送媒体の流れを示す動作図である。Operation mode No. of the air conditioning and hot water supply system shown in FIG. FIG. 6 is an operation diagram showing flows of the refrigerant and the heat transfer medium in 3; 図１に示す空調給湯システムの運転モードＮｏ．４－１における冷媒と熱搬送媒体の流れを示す動作図である。Operation mode No. of the air conditioning and hot water supply system shown in FIG. FIG. 10 is an operation diagram showing flows of a refrigerant and a heat transfer medium in 4-1. 図１に示す空調給湯システムの運転モードＮｏ．４－２における冷媒と熱搬送媒体の流れを示す動作図である。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. 図１に示す空調給湯システムの運転モードＮｏ．５における冷媒と熱搬送媒体の流れを示す動作図である。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; 図１に示す空調給湯システムの各運転モードの選択条件を示した図である。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. 空調給湯システムにおける冷媒の圧力－エンタルピ線図であり、図１０（ａ）は本発明の第１の実施の形態例に係る空調給湯システムにおける冷媒の圧力－エンタルピ線図であり、図１０（ｂ）は従来の空調給湯システムにおける冷媒の圧力－エンタルピ線図である。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, and FIG. 2.) is a pressure-enthalpy diagram of the refrigerant in the conventional air conditioning and hot water supply system. 本発明の第２の実施の形態例に係る空調給湯システムの系統図である。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. 本発明の第３の実施の形態例に係る空調給湯システムの系統図である。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.

　［本発明の第１の実施形態］
　本発明の第１の実施の形態例に係る空調給湯システムは、図１に示すように、冷房運転と暖房運転とを切り替えて運転を行う空調用冷媒回路５と、給湯を行う給湯用冷媒回路６と、空調用冷媒回路５と熱交換を行って、住宅６０の室内の空調を行う空調用冷温水循環回路（空調用熱搬送媒体循環回路）８と、給湯用冷媒回路６と熱交換を行って給湯を行う給湯回路９とを備えている。また、本発明の第１の実施の形態例に係る空調給湯システムは、室外に配置されるヒートポンプユニット１と、室内に配置される室内ユニット２とを備えたユニット構成となっている。 First Embodiment of the Present Invention
As shown in FIG. 1, the air conditioning and hot water supply system according to the first embodiment of the present invention 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.

　ヒートポンプユニット１には、空調用冷媒回路５、給湯用冷媒回路６、空調用冷温水循環回路８および給湯回路９が組み込まれている。さらに、空調用冷媒回路５と給湯用冷媒回路６との間には中間熱交換器２３が配置されている。この中間熱交換器２３は、空調用冷媒回路５を循環する空調用冷媒と、給湯用冷媒回路６を循環する給湯用冷媒との間で熱交換を行うことが可能な構造となっている。 In the heat pump unit 1, 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.

　空調用冷媒回路５は、空調用冷媒が循環することにより冷凍サイクルが形成される回路であり、空調用冷媒を圧縮する空調用圧縮機２１、空調用冷媒の流路を切り替える四方弁（空調用流路切替弁）２２、中間熱交換器２３、ファン（図示せず）により送られてくる大気と熱交換を行う空調用熱源側熱交換器２４、空調用冷媒タンク２６、空調用冷媒を減圧する空調用膨張弁２７、空調用冷温水循環回路８と熱交換を行う空調用利用側熱交換器２８を冷媒配管で接続して環状に形成されている。なお、中間熱交換器２３は、空調用利用側熱交換器２８よりも高い位置に設置されており、中間熱交換器２３と空調用利用側熱交換器２８との間にヘッド差が形成されている。このヘッド差によって、空調用冷媒を空調用冷媒回路５内で自然循環させることができるのである（詳しくは後述する）。 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. In addition, 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).

　次に、空調用冷媒回路５の構成の詳細を説明する。空調用冷媒回路５は、まず、空調用圧縮機２１の吐出口２１ｂ、四方弁２２、中間熱交換器２３、空調用冷媒タンク２６、空調用膨張弁２７、空調用利用側熱交換器２８、四方弁２２、空調用圧縮機２１の吸込口２１ａの順に冷媒配管で接続して環状に形成された空調用冷媒主回路５ａを備えている。 Next, details of the configuration of the air conditioning refrigerant circuit 5 will be described. 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.

　空調用冷媒回路５は、この空調用冷媒主回路５ａに２つの空調用冷媒分岐路５ｂ、５ｃが設けられて構成されている。第１の空調用冷媒分岐路５ｂは、中間熱交換器２３と並列に接続された空調用熱源側熱交換器２４を経由する空調用冷媒分岐路であり、具体的には、四方弁２２と中間熱交換器２３との間の位置にある分岐点Ｉから分岐し、空調用熱源側熱交換器２４を経由して、中間熱交換器２３と空調用冷媒タンク２６の間の位置にある分岐点Ｊで合流する空調用冷媒分岐路である。 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.

　第２の空調用冷媒分岐路５ｃは、空調用圧縮機２１の吸込口２１ａと吐出口２１ｂとをバイパスする空調用冷媒分岐路であり、具体的には、空調用利用側熱交換器２８と四方弁２２との間の位置にある分岐点Ａと、四方弁２２と分岐点Ｉの間の位置にある分岐点Ｂとを空調用冷媒バイパス配管（バイパス配管）２９で繋いで形成された空調用冷媒分岐路である。なお、分岐点Ａには三方弁３４ａが、分岐点Ｂには三方弁３４ｂがそれぞれ設けられており、これらの三方弁（バイパス開閉手段）３４ａ、３４ｂを操作することにより、空調用冷媒の流路が、空調用圧縮機２１を経由する流路と、空調用圧縮機２１をバイパスする流路の何れかに切り替わる。 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. By operating these three-way valves (bypass opening / closing means) 34a, 34b, the flow of air conditioning refrigerant The path is switched to either the flow path passing through the air conditioning compressor 21 or the flow path bypassing the air conditioning compressor 21.

　なお、二方弁３５ａ、３５ｂが中間熱交換器２３を挟んで設けられ、二方弁３５ｃ、３５ｄが空調用熱源側熱交換器２４を挟んで設けられている。また、空調用冷媒回路５を循環する空調用冷媒としては、例えば、Ｒ４１０ａ、Ｒ１３４ａ，ＨＦＯ１２３４ｙｆ，ＨＦＯ１２３４ｚｅ、ＣＯ２を用いることができる。 In addition, 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. Further, as the air conditioning refrigerant circulating in the air conditioning refrigerant circuit 5, for example, R410a, R134a, HFO1234yf, HFO1234ze, CO2 can be used.

　次に、上記した空調用冷媒回路５に組み込まれる各機器の構造について、詳細に説明する。空調用圧縮機２１は、容量制御が可能な可変容量型の圧縮機である。このような圧縮機としては、ピストン式、ロータリー式、スクロール式、スクリュー式、遠心式のものを採用可能である。具体的には、空調用圧縮機２１は、スクロール式の圧縮機であり、インバータ制御により容量制御が可能で、低速から高速まで回転速度が可変である。 Next, the structure of each device incorporated in the above-described air conditioning refrigerant circuit 5 will be described in detail. The air conditioning compressor 21 is a variable displacement compressor capable of capacity control. As such a compressor, a piston type, a rotary type, a scroll type, a screw type, or a centrifugal type can be employed. Specifically, 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.

　中間熱交換器２３は、図示しないが、空調用冷媒が流れる空調用冷媒伝熱管と給湯用冷媒が流れる給湯用冷媒伝熱管とがお互いに熱的に接触する（例えば、伝熱管同士を接合する）ように一体に構成された熱交換器である。また、空調用利用側熱交換器２８は、図示しないが、空調用冷媒が流れる空調用冷媒伝熱管と水（空調用利用側の熱搬送媒体）が流れる空調用冷温水伝熱管とが熱的に接触するように構成されている。空調用冷媒タンク２６は、流路の切替えによって変化する空調用冷媒の量を制御するバッファとして機能するものである。空調用膨張弁２７は、弁の開度を調整することにより、空調用冷媒の圧力を所定の圧力まで減圧することができる。 In the intermediate heat exchanger 23, although not shown, 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. Although 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.

　空調用冷温水循環回路（空調用熱搬送媒体循環回路）８は、空調用冷媒回路５と熱交換を行うための空調用利用側の熱搬送媒体として水が流れる回路であり、住宅（被空調空間）６０に設置された室内熱交換器６１、空調用冷温水循環ポンプ５２、四方弁５３、空調用利用側熱交換器２８を空調用冷温水配管で順次接続して、環状に形成された回路である。この空調用冷温水循環回路８内を流れる水（冷水または温水）は、室内熱交換器６１を介して住宅６０内の空気と熱交換して、住宅６０内を冷房または暖房する。なお、空調用冷温水循環回路８内を流れる空調用利用側の熱搬送媒体として、水の代わりにエチレングリコールなどのブラインを用いても良い。ブラインを用いると寒冷地でも適用できることは言うまでもない。 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. In addition, you may use brine, such as ethylene glycol, instead of water as a heat conveyance medium of the utilization side by the side of air-conditioning which flows through the inside of the cold / hot water circulation circuit 8 for air conditioning. It goes without saying that use in brine is also applicable in cold regions.

　なお、以下の説明において、空調用冷温水循環回路８を流れる水として「冷水」または「温水」という言葉が用いられることがあるが、「冷水」とは冷房時に空調用冷温水循環回路８を流れる水の意味で用いられ、「温水」とは暖房時に空調用冷温水循環回路８を流れる水の意味で用いられていることを、ここで付言しておく。 In the following description, the words “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. Here, it is added that “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.

　給湯用冷媒回路６は、給湯用冷媒が循環することにより冷凍サイクルが形成される回路であり、給湯用冷媒を圧縮する給湯用圧縮機４１、給湯回路９と熱交換を行う給湯用利用側熱交換器４２、給湯用冷媒タンク４６、給湯用冷媒を減圧する給湯用膨張弁４３、中間熱交換器２３、およびファン（図示せず）により送られてくる大気と熱交換を行う給湯用熱源側熱交換器４４を冷媒配管で接続して環状に形成されている。 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.

　次に、給湯用冷媒回路６の構成の詳細を説明する。給湯用冷媒回路６は、まず、給湯用圧縮機４１の吐出口４１ｂ、給湯用利用側熱交換器４２、給湯用冷媒タンク４６、給湯用膨張弁４３、中間熱交換器２３、給湯用圧縮機４１の吸込口４１ａの順に冷媒配管で接続して環状に形成された給湯用冷媒主回路６ａを備えている。 Next, details of the configuration of the hot water supply refrigerant circuit 6 will be described. First, 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.

　給湯用冷媒回路６は、この給湯用冷媒主回路６ａに給湯用冷媒分岐路６ｂが設けられて構成されている。給湯用冷媒分岐路６ｂは、中間熱交換器２３と並列に接続された給湯用熱源側熱交換器４４を経由する給湯用冷媒分岐路であり、具体的には、給湯用膨張弁４３と中間熱交換器２３の間の位置にある分岐点Ｋから分岐し、給湯用熱源側熱交換器４４を経由して、中間熱交換器２３と給湯用圧縮機４１の吸込口４１ａの間の位置にある分岐点Ｌで合流する給湯用冷媒分岐路である。 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.

　なお、中間熱交換器２３の入口の近傍位置には二方弁４９ｂが、給湯用熱源側熱交換器４４の入口の近傍位置には二方弁４９ａが、それぞれ設けられている。また、給湯用冷媒回路６を循環する給湯用冷媒としては、例えば、Ｒ１３４ａ，ＨＦＯ１２３４ｙｆ，ＨＦＯ１２３４ｚｅ、ＣＯ２を用いることができる。 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. Further, as the hot water supply refrigerant circulating through the hot water supply refrigerant circuit 6, for example, R134a, HFO1234yf, HFO1234ze, CO2 can be used.

　次に、上記した給湯用冷媒回路６に組み込まれる各機器の構造について、詳細に説明する。給湯用圧縮機４１は、空調用圧縮機２１と同様にインバータ制御により容量制御が可能で、低速から高速まで回転速度が可変である。給湯用利用側熱交換器４２は、図示しないが、給湯回路９に供給される水が流れる給湯用水伝熱管と、給湯用冷媒が流れる給湯用冷媒伝熱管とが熱的に接触するように構成されている。給湯用膨張弁４３は、弁の開度を調整することにより、給湯用冷媒の圧力を所定の圧力まで減圧することができる。 Next, the structure of each device incorporated in the above-described refrigerant circuit 6 for hot water supply will be described in detail. Similarly to the air conditioning compressor 21, 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. Although not shown, 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.

　給湯回路９は、給湯用利用側熱交換器４２の入口に給湯用配管７２の一端を接続し、給湯用利用側熱交換器４２の出口に給湯用配管７３の一端を接続して形成された回路である。給湯用配管７２の他端は水の供給元と接続され、給湯用配管７３の他端は給湯負荷側の機器（浴槽など）と接続されている。よって、給湯回路９内に供給された水は、給湯用利用側熱交換器４２と熱交換を行うことにより温水となり、給湯用配管７３を流れながら給湯負荷側の機器へと導かれる。なお、給湯回路９には、図示しないが、給湯用循環ポンプと、水の流量を検知する給湯用流量センサとが組み込まれている。なお、給湯用利用側熱交換器４２において、給湯用冷媒の流れと水の流れは対向流となっている。 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. Although not shown, 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. In the hot water use side heat exchanger 42, the flow of the hot water supply refrigerant and the flow of water are opposite to each other.

　なお、この空調給湯システムには、複数の温度センサＴＥ１～ＴＥ８を備えている。具体的には、空調用冷温水循環回路８には、空調用利用側熱交換器２８の入口（冷房運転時における入口）に温度センサＴ１が、出口（冷房運転時における出口）に温度センサＴＥ２がそれぞれ設けられている。空調用冷媒回路５には、空調用圧縮機２１の吸込口２１ａに温度センサＴＥ３が、吐出口２１ｂに温度センサＴＥ４がそれぞれ設けられている。また、給湯回路９には、給湯用利用側熱交換器４２の入口に温度センサＴＥ７が、出口に温度センサＴＥ８がそれぞれ設けられている。なお、図示しないが、外気温度を測定するための外気温度センサも設けられている。 The air conditioning and hot water supply system is provided with a plurality of temperature sensors TE1 to TE8. Specifically, in the cold / hot water circulation circuit 8 for air conditioning, 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). Each is provided. In the air conditioning refrigerant circuit 5, 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. Further, in the hot water supply circuit 9, 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. Although not shown, an outside air temperature sensor for measuring the outside air temperature is also provided.

　制御装置１ａは、図示しないリモコンからの指令信号、温度センサＴＥ１～ＴＥ８および外気温度センサの検知信号などを入力し、これらの入力信号に基づいて、空調用圧縮機２１および給湯用圧縮機４１の駆動／停止、四方弁２２、５３の切り替え、空調用膨張弁２７および給湯用膨張弁４３の弁の開度の調整、三方弁３４ａ、３４ｂの切り替え、空調用冷温水循環ポンプ５２の駆動／停止、二方弁３５ａ～３５ｄ、二方弁４９ａ、４９ｂの開閉、その他の空調給湯システムの運転に必要な制御を行っている。 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.

　続いて、上記した空調給湯システムによって行われる各種運転モードについて図２～図８を参照しながら説明する。図２～図８において、熱交換器に付された矢印は熱の流れを示しており、各回路５、６、８、９に付された矢印は、流体が各回路を流れる向きを示している。また、図２～図８において、二方弁については、黒色に塗られたものは閉状態であることを示しており、三方弁については、黒く塗られたポートは閉じていることを示しており、四方弁については、実線の流路が有効となっていることを示している。なお、図２～図８において、温度センサＴＥ１～ＴＥ８の図示は省略している。 Subsequently, various operation modes performed by the above-described air conditioning and hot water supply system will be described with reference to FIGS. 2 to 8. In 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.

　「運転モードＮｏ．１＜冷房／給湯運転＞」（図２参照）
　運転モードＮｏ．１は、空調用冷媒回路５による冷房運転と、給湯用冷媒回路６による給湯運転とをそれぞれ行う運転モードである。 "Operation mode No. 1 <cooling / hot-water supply operation>" (see Fig. 2)
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.

　空調用冷媒回路５では、空調用圧縮機２１の吐出口２１ｂより吐出された高温高圧のガス冷媒は、四方弁２２を通って、空調用熱源側熱交換器２４に流入する。空調用熱源側熱交換器２４内を流れる高温高圧のガス冷媒は、大気へ放熱して凝縮し、液化する。この高圧の冷媒は、所定の開度に調節された空調用膨張弁２７で減圧、膨張し、低温低圧の気液二相冷媒となり、空調用利用側熱交換器２８に流入する。空調用利用側熱交換器２８内を流れる気液二相冷媒は、空調用冷温水循環回路８内を流れる冷水から吸熱して蒸発し、低圧のガス冷媒となる。この低圧のガス冷媒は、四方弁２２を通って、空調用圧縮機２１の吸込口２１ａに流入し、空調用圧縮機２１により再び圧縮されて高温高圧のガス冷媒となる。 In the air conditioning refrigerant circuit 5, 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.

　なお、運転モードＮｏ．１では、中間熱交換器２３の前後の二方弁３５ａ、３５ｂは閉じており、空調用冷媒が中間熱交換器２３内を流れないようになっている。また、空調用圧縮機２１の前後の三方弁３４ａ、３４ｂにより、空調用圧縮機２１をバイパスする第２の空調用冷媒分岐路５ｃは閉鎖されている。 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.

　空調用冷温水循環回路８では、空調用利用側熱交換器２８を流れる空調用冷媒に放熱した冷水は、空調用冷温水循環ポンプ５２を駆動することにより、空調用冷温水配管を通って、室内熱交換器６１に流入する。室内熱交換器６１では、空調用冷温水循環回路８内の冷水と、住宅６０内の高温の空気とで熱交換が行われ、住宅６０の空気が冷却される。つまり、住宅６０の室内が冷房される。このとき、室内熱交換器６１を流れる冷水は、住宅６０内の空気から吸熱して昇温される。この昇温された冷水は、空調用冷温水循環ポンプ５２により空調用冷温水循環回路８内を循環し、再び空調用利用側熱交換器２８を流れる間に空調用冷媒回路５と熱交換を行って、所定温度まで冷却される。 In the air conditioning cold and hot water circulation circuit 8, 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. In 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.

　一方、給湯用冷媒回路６では、給湯用圧縮機４１で圧縮され高温高圧となったガス冷媒は、給湯用利用側熱交換器４２に流入する。給湯用利用側熱交換器４２内を流れる高温高圧のガス冷媒は、給湯回路９内を流れる水へ放熱して凝縮し、液化する。このとき、給湯回路９では、給湯用利用側熱交換器４２で給湯用冷媒回路６から温熱を受け取ることにより、供給された水が所定温度の湯となる。そして、液化した高圧の冷媒は、所定の開度に調節された給湯用膨張弁４３で減圧、膨張して、低温低圧の気液二相冷媒となる。この気液二相冷媒は、給湯用熱源側熱交換器４４を流れる間に、大気から吸熱して蒸発し、低圧のガス冷媒となる。この低圧のガス冷媒は、給湯用圧縮機４１の吸込口４１ａに流入し、給湯用圧縮機４１により再び圧縮されて高温高圧のガス冷媒となる。 On the other hand, in the hot water supply refrigerant circuit 6, 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. At this time, in the hot water supply circuit 9, 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. Then, 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. While flowing through the heat source side heat exchanger 44 for hot water supply, 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.

　なお、運転モードＮｏ．１では、中間熱交換器２３の上流側の二方弁４９ｂは閉じており、給湯用冷媒が中間熱交換器２３内を流れないようになっている。 Operation mode No. In No. 1, the two-way valve 49b on the upstream side of the intermediate heat exchanger 23 is closed, so that the hot water supply refrigerant does not flow in the intermediate heat exchanger 23.

　「運転モードＮｏ．２－１＜冷房排熱を利用した給湯運転＞」（図３参照）
　運転モードＮｏ．２－１は、冷房運転による排熱を利用して給湯運転を行うモードのうち、冷房運転による排熱が給湯運転による吸熱より大きい場合に行われる運転モードである。この運転モードＮｏ．２－１は、冷房運転による排熱が給湯運転による吸熱より大きい場合に行われるモードであるため、給湯用熱源側熱交換器４４を使用しなくても済む。そのため、給湯用熱源側熱交換器４４の上流側の二方弁４９ａは閉じて、給湯用冷媒が給湯用熱源側熱交換器４４内を流れないようにしている。 "Operation mode No. 2-1 <Hot water supply operation using cooling exhaust heat>" (see Fig. 3)
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. This operation mode No. Since 2-1 is a mode performed when the exhaust heat by the cooling operation is larger than the heat absorption by the hot water supply operation, it is not necessary to use the heat source side heat exchanger 44 for hot water supply. Therefore, the two-way valve 49a on the upstream side of the hot water supply heat source side heat exchanger 44 is closed so that the hot water supply refrigerant does not flow in the hot water supply heat source side heat exchanger 44.

　空調用冷媒回路５では、空調用圧縮機２１の吐出口２１ｂより吐出された高温高圧のガス冷媒は、四方弁２２を通って、空調用熱源側熱交換器２４と中間熱交換器２３に分かれて流入する。つまり、ガス冷媒は、空調用冷媒主回路５ａと第１の空調用冷媒分岐路５ｂとに分岐して流れていく。空調用熱源側熱交換器２４内を流れる高温高圧のガス冷媒は、大気へ放熱して凝縮し、液化する。一方、中間熱交換器２３内を流れる高温高圧のガス冷媒は、給湯用回路６内を流れる給湯用冷媒へ放熱することで凝縮し、液化する。つまり、中間熱交換器２３内において、空調用冷媒と給湯用冷媒とによる熱交換が行われるのである。 In the air conditioning refrigerant circuit 5, 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. On the other hand, 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.

　空調用熱源側熱交換器２４および中間熱交換器２３からそれぞれ流出した高圧の冷媒は、所定の開度に調節された空調用膨張弁２７で減圧、膨張し、低温低圧の気液二相冷媒となり、空調用利用側熱交換器２８に流入する。空調用利用側熱交換器２８内を流れる気液二相冷媒は、空調用冷温水循環回路８内を流れる冷水から吸熱して蒸発し、低圧のガス冷媒となる。この低圧のガス冷媒は、四方弁２２を通って、空調用圧縮機２１の吸込口２１ａに流入し、空調用圧縮機２１により再び圧縮されて高温高圧のガス冷媒となる。 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.

　なお、運転モードＮｏ．２－１では、空調用圧縮機２１の前後の三方弁３４ａ、３４ｂにより、空調用圧縮機２１をバイパスする第２の空調用冷媒分岐路５ｃは閉鎖されている。 Operation mode No. In 2-1, the second air conditioning refrigerant branch passage 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.

　空調用冷温水循環回路８では、空調用利用側熱交換器２８を流れる空調用冷媒に放熱した冷水は、空調用冷温水循環ポンプ５２を駆動することにより、空調用冷温水配管を通って、室内熱交換器６１に流入する。室内熱交換器６１では、空調用冷温水循環回路８内の冷水と、住宅６０内の高温の空気とで熱交換が行われ、住宅６０の空気が冷却される。つまり、住宅６０の室内が冷房される。このとき、室内熱交換器６１を流れる冷水は、住宅６０内の空気から吸熱して昇温される。この昇温された冷水は、空調用冷温水循環ポンプ５２により空調用冷温水循環回路８内を循環し、再び空調用利用側熱交換器２８を流れる間に空調用冷媒回路５と熱交換を行って、所定温度まで冷却される。 In the air conditioning cold and hot water circulation circuit 8, 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. In 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.

　一方、給湯用冷媒回路６では、給湯用圧縮機４１で圧縮され高温高圧となったガス冷媒は、給湯用利用側熱交換器４２に流入する。給湯用利用側熱交換器４２内を流れる高温高圧のガス冷媒は、給湯回路９内を流れる水へ放熱して凝縮し、液化する。このとき、給湯回路９では、給湯用利用側熱交換器４２で給湯用冷媒回路６から温熱を受け取ることにより、供給された水が所定温度の湯となる。そして、液化した高圧の冷媒は、給湯用膨張弁４３で減圧、膨張して、低温低圧の気液二相冷媒となる。この気液二相冷媒は、中間熱交換器２３を流れる間に、空調用冷媒から吸熱して蒸発し、低圧のガス冷媒となる。つまり、中間熱交換器２３内において、空調用冷媒と給湯用冷媒とによる熱交換が行われるのである。この低圧のガス冷媒は、給湯用圧縮機４１の吸込口４１ａに流入し、給湯用圧縮機４１により再び圧縮されて高温高圧のガス冷媒となる。この運転モードＮｏ．２－１では、給湯用冷媒回路６における中間熱交換器２３は、空調用冷媒回路５の排熱を利用した蒸発器として機能することとなる。 On the other hand, in the hot water supply refrigerant circuit 6, 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. At this time, in the hot water supply circuit 9, 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. Then, 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. While flowing through the intermediate heat exchanger 23, 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.

　この運転モードＮｏ．２－１では、空調用冷媒回路５の冷房運転で生じた排熱を利用して、給湯用冷媒回路６による給湯サイクル運転を行うことができるため、エネルギの有効利用が図れることとなる。また、この運転モードＮｏ．２－１は、空調排熱を熱源として利用しているため、外気を熱源として利用する場合に比べて、給湯サイクルの蒸発温度を上げることができる。よって、運転モードＮｏ．２－１では、給湯用圧縮機４１への入力を低減できるので、給湯用圧縮機４１の消費電力を低減することができる。さらに、運転モードＮｏ．２－１では、給湯用熱源側熱交換器４４のファンを停止することができることからも、給湯サイクルの運転に掛かる消費電力は低減する。 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.

　「運転モードＮｏ．２－２＜冷房排熱を利用した給湯運転＞」（図４参照）
　運転モードＮｏ．２－２は、冷房運転による排熱を利用して給湯運転を行うモードのうち、冷房運転による排熱が給湯運転による吸熱より小さい場合に行われる運転モードである。この運転モードＮｏ．２－２は、冷房運転による排熱が給湯運転による吸熱より小さい場合に行われるモードであるため、空調用熱源側熱交換器２４を使用しなくても済む。そのため、空調用熱源側熱交換器２４の前後の二方弁３５ｃ、３５ｄは閉じて、空調用冷媒が空調用熱源側熱交換器２４内を流れないようにしている。 "Operation mode No. 2-2 <Hot water supply operation using cooling exhaust heat>" (see Fig. 4)
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.

　空調用冷媒回路５では、空調用圧縮機２１の吐出口２１ｂより吐出された高温高圧のガス冷媒は、四方弁２２を通って、中間熱交換器２３に流入する。中間熱交換器２３内を流れる高温高圧のガス冷媒は、給湯用回路６内を流れる給湯用冷媒へ放熱することで凝縮し、液化する。つまり、中間熱交換器２３内において、空調用冷媒と給湯用冷媒とによる熱交換が行われるのである。 In the air conditioning refrigerant circuit 5, 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.

　そして、この高圧の冷媒は、所定の開度に調節された空調用膨張弁２７で減圧、膨張し、低温低圧の気液二相冷媒となり、空調用利用側熱交換器２８に流入する。空調用利用側熱交換器２８内を流れる気液二相冷媒は、空調用冷温水循環回路８内を流れる冷水から吸熱して蒸発し、低圧のガス冷媒となる。この低圧のガス冷媒は、四方弁２２を通って、空調用圧縮機２１の吸込口２１ａに流入し、空調用圧縮機２１により再び圧縮されて高温高圧のガス冷媒となる。 Then, 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.

　なお、運転モードＮｏ．２－２では、空調用圧縮機２１の前後の三方弁３４ａ、３４ｂにより、空調用圧縮機２１をバイパスする第２の空調用冷媒分岐路５ｃは閉鎖されている。 Operation mode No. In 2-2, the second air conditioning refrigerant branch passage 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.

　空調用冷温水循環回路８では、空調用利用側熱交換器２８を流れる空調用冷媒に放熱した冷水は、空調用冷温水循環ポンプ５２を駆動することにより、空調用冷温水配管を通って、室内熱交換器６１に流入する。室内熱交換器６１では、空調用冷温水循環回路８内の冷水と、住宅６０内の高温の空気とで熱交換が行われ、住宅６０の空気が冷却される。つまり、住宅６０の室内が冷房される。このとき、室内熱交換器６１を流れる冷水は、住宅６０内の空気から吸熱して昇温される。この昇温された冷水は、空調用冷温水循環ポンプ５２により空調用冷温水循環回路８内を循環し、再び空調用利用側熱交換器２８を流れる間に空調用冷媒回路５と熱交換を行って、所定温度まで冷却される。 In the air conditioning cold and hot water circulation circuit 8, 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. In 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.

　一方、給湯用冷媒回路６では、給湯用圧縮機４１で圧縮され高温高圧となったガス冷媒は、給湯用利用側熱交換器４２に流入する。給湯用利用側熱交換器４２内を流れる高温高圧のガス冷媒は、給湯回路９内を流れる水へ放熱して凝縮し、液化する。このとき、給湯回路９では、給湯用利用側熱交換器４２で給湯用冷媒回路６から温熱を受け取ることにより、供給された水が所定温度の湯となる。そして、液化した高圧の冷媒は、給湯用膨張弁４３で減圧、膨張して、低温低圧の気液二相冷媒となる。この気液二相冷媒は、給湯用熱源側熱交換器４４と中間熱交換器２３に分かれて流入する。つまり、ガス冷媒は、給湯用冷媒主回路６ａと給湯用冷媒分岐路６ｂとに分岐して流れていく。給湯用熱源側熱交換器４４内を流れる気液二相冷媒は、大気から吸熱して蒸発し、低圧のガス冷媒となる。 On the other hand, in the hot water supply refrigerant circuit 6, 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. At this time, in the hot water supply circuit 9, 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. Then, 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.

　一方、中間熱交換器２３内を流れる気液二相冷媒は、空調用回路５内を流れる空調用冷媒から吸熱して蒸発し、低圧のガス冷媒となる。つまり、中間熱交換器２３内において、空調用冷媒と給湯用冷媒とによる熱交換が行われるのである。給湯用熱源側熱交換器４４および中間熱交換器２３からそれぞれ流出した低圧のガス冷媒は、給湯用圧縮機４１の吸込口４１ａに流入し、給湯用圧縮機４１により再び圧縮されて高温高圧のガス冷媒となる。この運転モードＮｏ．２－２では、給湯用冷媒回路６における中間熱交換器２３は、空調用冷媒回路５の排熱を利用した蒸発器として機能することとなる。 On the other hand, 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. This operation mode No. In 2-2, 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.

　この運転モードＮｏ．２－２では、空調用冷媒回路５の冷房運転で生じた空調排熱を給湯用冷媒回路６へ放熱することができるため、空調排熱を外気に放熱するのに比べて、空調サイクルの凝縮圧力を下げることができるため、空調用圧縮機２１の入力を低減することができる。よって、運転モードＮｏ．２－２では、空調用圧縮機２１の消費電力を低減することができる。さらに、運転モードＮｏ．２－２では、空調用熱源側熱交換器２４のファンを停止することができることからも、空調サイクルの運転に掛かる消費電力は低減する。 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.

　「運転モードＮｏ．３＜暖房／給湯運転＞」（図５参照）
　運転モードＮｏ．３は、空調用冷媒回路５による暖房運転と、給湯用冷媒回路６による給湯運転とをそれぞれ行うモードである。 "Operation mode No. 3 <heating / hot-water supply operation>" (see Fig. 5)
Operation mode No. A mode 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.

　空調用冷媒回路５では、空調用圧縮機２１の吐出口２１ｂより吐出された高温高圧のガス冷媒は、四方弁２２を通って、空調用利用側熱交換器２８に流入する。空調用利用側熱交換器２８内を流れる高温高圧のガス冷媒は、空調用冷温水回路８内を流れる温水へ放熱して凝縮し、液化する。この高圧の冷媒は、所定の開度に調節された空調用膨張弁２７で減圧、膨張し、低温低圧の気液二相冷媒となり、空調用熱源側熱交換器２４に流入する。空調用熱源側熱交換器２４内を流れる気液二相冷媒は、大気から吸熱して蒸発し、低圧のガス冷媒となる。この低圧のガス冷媒は、四方弁２２を通って、空調用圧縮機２１の吸込口２１ａに流入し、空調用圧縮機２１により再び圧縮されて高温高圧のガス冷媒となる。 In the air conditioning refrigerant circuit 5, 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.

　なお、運転モードＮｏ．３では、中間熱交換器２３の前後の二方弁３５ａ、３５ｂは閉じており、空調用冷媒が中間熱交換器２３内を流れないようになっている。また、空調用圧縮機２１の前後の三方弁３４ａ、３４ｂにより、空調用圧縮機２１をバイパスする第２の空調用冷媒分岐路５ｃは閉鎖されている。 Operation mode No. In 3, 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.

　空調用冷温水循環回路８では、空調用利用側熱交換器２８を流れる空調用冷媒から吸熱した温水は、空調用冷温水循環ポンプ５２を駆動することにより、空調用冷温水配管を通って、室内熱交換器６１に流入する。室内熱交換器６１では、空調用冷温水循環回路８内の温水と、住宅６０内の低温の空気とで熱交換が行われ、住宅６０の空気が加熱される。つまり、住宅６０の室内が暖房される。このとき、室内熱交換器６１を流れる温水は、住宅６０内の空気へ放熱して冷却される。この冷却された温水は、空調用冷温水循環ポンプ５２により空調用冷温水循環回路８内を循環し、再び空調用利用側熱交換器２８を流れる間に空調用冷媒回路５と熱交換を行って、所定温度まで昇温される。 In the air conditioning cold / hot water circulation circuit 8, 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. In 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.

　一方、給湯用冷媒回路６では、給湯用圧縮機４１で圧縮され高温高圧となったガス冷媒は、給湯用利用側熱交換器４２に流入する。給湯用利用側熱交換器４２内を流れる高温高圧のガス冷媒は、給湯回路９内を流れる水へ放熱して凝縮し、液化する。このとき、給湯回路９では、給湯用利用側熱交換器４２で給湯用冷媒回路６から温熱を受け取ることにより、供給された水が所定温度の湯となる。そして、液化した高圧の冷媒は、所定の開度に調節された給湯用膨張弁４３で減圧、膨張して、低温低圧の気液二相冷媒となる。この気液二相冷媒は、給湯用熱源側熱交換器４４を流れる間に、大気から吸熱して蒸発し、低圧のガス冷媒となる。この低圧のガス冷媒は、給湯用圧縮機４１の吸込口４１ａに流入し、給湯用圧縮機４１により再び圧縮されて高温高圧のガス冷媒となる。 On the other hand, in the hot water supply refrigerant circuit 6, 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. At this time, in the hot water supply circuit 9, 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. Then, 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. While flowing through the heat source side heat exchanger 44 for hot water supply, 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.

　なお、運転モードＮｏ．３では、中間熱交換器２３の上流側の二方弁４９ｂは閉じており、給湯用冷媒が中間熱交換器２３内を流れないようになっている。 Operation mode No. In 3, the two-way valve 49b on the upstream side of the intermediate heat exchanger 23 is closed so that the hot water supply refrigerant does not flow in the intermediate heat exchanger 23.

　「運転モードＮｏ．４－１＜給湯サイクルを利用した空調側自然循環運転＞」（図６参照）
　運転モードＮｏ．４－１は、給湯用冷媒回路６による給湯運転を行いながら空調用冷媒回路５内の空調用冷媒を自然循環させて冷房運転を行う運転モードのうち、冷房運転による排熱が給湯運転による吸熱より大きい場合に行われる運転モードである。この運転モードＮｏ．４－１は、冷房運転による排熱が給湯運転による吸熱より大きい場合に行われるモードであるため、給湯用熱源側熱交換器４４を使用しなくても済む。そのため、給湯用熱源側熱交換器４４の上流側の二方弁４９ａは閉じて、給湯用冷媒が給湯用熱源側熱交換器４４内を流れないようにしている。 "Operation mode No. 4-1 <natural circulation operation on the air conditioning side using the hot water supply cycle>" (see Fig. 6)
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. Since 4-1 is a mode performed when the exhaust heat by the cooling operation is larger than the heat absorption by the hot water supply operation, it is not necessary to use the heat source side heat exchanger 44 for hot water supply. Therefore, the two-way valve 49a on the upstream side of the hot water supply heat source side heat exchanger 44 is closed so that the hot water supply refrigerant does not flow in the hot water supply heat source side heat exchanger 44.

　この運転モードＮｏ．４－１では、空調用圧縮機２１が停止しており、空調用圧縮機２１の前後の三方弁３４ａ、３４ｂにより、空調用圧縮機２１をバイパスする第２の空調用冷媒分岐路５ｃが開放され、空調用圧縮機２１を経由する経路（図６において点線で示す経路）が閉鎖されている。そのため、空調用冷媒は、空調用圧縮機２１をバイパスして空調用冷媒回路５内を循環する。なお、運転モードＮｏ．４－１では、中間熱交換器２３の前後の二方弁３５ａ、３５ｂは開いている。なお、空調用膨張弁２７は、空調用利用側熱交換器２８で得たい交換熱量に応じて所定の開度に調整されている。 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.

　中間熱交換器２３内に滞留している空調用冷媒は、給湯用冷媒回路６を流れる給湯用冷媒へ放熱して凝縮し、液化する。密度の大きい液冷媒は、重力の影響を受けて下降していき、空調用膨張弁２７を通り、空調用利用側熱交換器２８を流れる間に空調用冷温水循環回路８内を循環する冷水から吸熱して蒸発し、ガス化する。このとき、冷媒の密度差による圧力勾配ができるため、蒸発した冷媒は、中間熱交換器２３に向かって流れていく。空調用熱源側熱交換器２４内に滞留している空調用冷媒についても、同様に、大気へ放熱して凝縮し、液化することで、密度差による空調用冷媒回路５内の自然循環が行われることとなる。このように、空調用冷媒回路５には、空調用冷媒が自然循環する自然循環サイクルが形成されているのである。 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. Similarly, 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.

　空調用冷温水循環回路８では、空調用利用側熱交換器２８を流れる空調用冷媒に放熱した冷水は、空調用冷温水循環ポンプ５２を駆動することにより、空調用冷温水配管を通って、室内熱交換器６１に流入する。室内熱交換器６１では、空調用冷温水循環回路８内の冷水と、住宅６０内の高温の空気とで熱交換が行われ、住宅６０の空気が冷却される。つまり、住宅６０の室内が冷房されることとなる。このとき、室内熱交換器６１を流れる冷水は、住宅６０内の空気から吸熱して昇温される。この昇温された冷水は、空調用冷温水循環ポンプ５２により空調用冷温水循環回路８内を循環し、再び空調用利用側熱交換器２８を流れる間に空調用冷媒回路５と熱交換を行って、所定温度まで冷却される。 In the air conditioning cold and hot water circulation circuit 8, 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. In 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.

　一方、給湯用冷媒回路６では、給湯用圧縮機４１で圧縮され高温高圧となったガス冷媒は、給湯用利用側熱交換器４２に流入する。給湯用利用側熱交換器４２内を流れる高温高圧のガス冷媒は、給湯回路９内を流れる水へ放熱して凝縮し、液化する。このとき、給湯回路９では、給湯用利用側熱交換器４２で給湯用冷媒回路６から温熱を受け取ることにより、供給された水が所定温度の湯となる。そして、液化した高圧の冷媒は、給湯用膨張弁４３で減圧、膨張して、低温低圧の気液二相冷媒となる。この気液二相冷媒は、中間熱交換器２３を流れる間に、空調用冷媒から吸熱して蒸発し、低圧のガス冷媒となる。つまり、中間熱交換器２３内において、空調用冷媒と給湯用冷媒とによる熱交換が行われるのである。この低圧のガス冷媒は、給湯用圧縮機４１の吸込口４１ａに流入し、給湯用圧縮機４１により再び圧縮されて高温高圧のガス冷媒となる。この運転モードでは、給湯用冷媒回路６における中間熱交換器２３は、空調用冷媒回路５を自然循環する空調用冷媒の熱を利用した蒸発器として機能することとなる。 On the other hand, in the hot water supply refrigerant circuit 6, 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. At this time, in the hot water supply circuit 9, 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. Then, 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. While flowing through the intermediate heat exchanger 23, 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. In this operation mode, 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.

　この運転モードＮｏ．４－１では、空調用圧縮機２１を運転することなく、空調用冷媒を自然循環させて、住宅６０内を冷房できるので、消費電力を大幅に低減できる。 This operation mode No. In 4-1, since the air conditioning refrigerant can be naturally circulated and the inside of the house 60 can be cooled without operating the air conditioning compressor 21, power consumption can be significantly reduced.

　ここで、住宅６０内を効率よく冷房するためには、空調用冷媒の自然循環が連続して行われていかなければならないが、外気温度と住宅６０内の温度（室内温度）との差が小さい場合には、冷媒の密度差が小さくなり、自然循環による運転を安定して行うことが難しくなってしまう。しかし、運転モードＮｏ．４－１では、給湯用冷媒回路６による給湯運転が行われているため、中間熱交換器２３内に滞留している空調用冷媒は、中間熱交換器２３内を流れる給湯用冷媒によって強制的に熱を奪われるため、凝縮して液化し易くなる。つまり、給湯運転で得た給湯用冷媒の熱（冷熱）により、空調用冷媒の自然循環がアシストされるのである。そのため、空調用冷媒の自然循環による冷房の効率は良くなり、住宅６０内は快適なものとなる。 Here, in order to efficiently cool the inside of the house 60, natural circulation of the air conditioning refrigerant must be performed continuously, but the difference between the outside air temperature and the temperature inside the house 60 (room temperature) is When it is small, the density difference of the refrigerant becomes small, and it becomes difficult to stably operate by natural circulation. However, the operation mode No. In 4-1, since the hot water supply operation by the hot water supply refrigerant circuit 6 is performed, the air conditioning refrigerant accumulated in the intermediate heat exchanger 23 is forced by the hot water supply refrigerant flowing in the intermediate heat exchanger 23. Because it takes heat away, it becomes easy to condense and liquefy. That is, 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.

　「運転モードＮｏ．４－２＜給湯サイクルを利用した空調側自然循環運転＞」（図７参照）
　運転モードＮｏ．４－２は、給湯用冷媒回路６による給湯運転を行いながら空調用冷媒回路５内の空調用冷媒を自然循環させて冷房運転を行うモードのうち、冷房運転による排熱が給湯運転による吸熱より小さい場合に行われる運転モードである。この運転モードＮｏ．４－２は、冷房運転による排熱が給湯運転による吸熱より小さい場合に行われるモードであるため、空調用熱源側熱交換器２４を使用しなくても済む。そのため、空調用熱源側熱交換器４４の前後の二方弁３５ｃ、３５ｄを閉じて、空調用冷媒が空調用熱源側熱交換器２４内を流れないようにしている。 "Operation mode No. 4-2 <Air conditioning side natural circulation operation using the hot water supply cycle>" (see Fig. 7)
Operation mode No. In 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. This operation mode No. Since 4-2 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 air conditioning heat source side heat exchanger 44 are closed so that the air conditioning refrigerant does not flow in the air conditioning heat source side heat exchanger 24.

　この運転モードＮｏ．４－２では、空調用圧縮機２１が停止しており、空調用圧縮機２１の前後の三方弁３４ａ、３４ｂにより、空調用圧縮機２１をバイパスする第２の空調用冷媒分岐路５ｃが開放され、空調用圧縮機２１を経由する経路（図７において点線で示す経路）が閉鎖されている。そのため、空調用冷媒は、空調用圧縮機２１をバイパスして空調用冷媒回路５内を循環する。なお、空調用膨張弁２７は、空調用利用側熱交換器２８で得たい交換熱量に応じて所定の開度に調整されている。 This operation mode No. In 4-2, 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. Thus, 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.

　中間熱交換器２３内に滞留している空調用冷媒は、給湯用冷媒回路６を流れる給湯用冷媒へ放熱して凝縮し、液化する。密度の大きい液冷媒は、重力の影響を受けて下降していき、空調用膨張弁２７を通り、空調用利用側熱交換器２８を流れる間に空調用冷温水循環回路８内を循環する冷水から吸熱して蒸発し、ガス化する。このとき、冷媒の密度差による圧力勾配ができるため、蒸発した冷媒は、中間熱交換器２３に向かって流れていく。このように、空調用冷媒回路５は、空調用冷媒が自然循環する自然循環サイクルが形成されているのである。 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. As described above, the air conditioning refrigerant circuit 5 is formed with a natural circulation cycle in which the air conditioning refrigerant naturally circulates.

　空調用冷温水循環回路８では、空調用利用側熱交換器２８を流れる空調用冷媒に放熱した冷水は、空調用冷温水循環ポンプ５２を駆動することにより、空調用冷温水配管を通って、室内熱交換器６１に流入する。室内熱交換器６１では、空調用冷温水循環回路８内の冷水と、住宅６０内の高温の空気とで熱交換が行われ、住宅６０の空気が冷却される。つまり、住宅６０の室内が冷房されることとなる。このとき、室内熱交換器６１を流れる冷水は、住宅６０内の空気から吸熱して昇温される。この昇温された冷水は、空調用冷温水循環ポンプ５２により空調用冷温水循環回路８内を循環し、再び空調用利用側熱交換器２８を流れる間に空調用冷媒回路５と熱交換を行って、所定温度まで冷却される。 In the air conditioning cold and hot water circulation circuit 8, 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. In 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.

　一方、給湯用冷媒回路６では、給湯用圧縮機４１で圧縮され高温高圧となったガス冷媒は、給湯用利用側熱交換器４２に流入する。給湯用利用側熱交換器４２内を流れる高温高圧のガス冷媒は、給湯回路９内を流れる水へ放熱して凝縮し、液化する。このとき、給湯回路９では、給湯用利用側熱交換器４２で給湯用冷媒回路６から温熱を受け取ることにより、供給された水が所定温度の湯となる。そして、液化した高圧の冷媒は、給湯用膨張弁４３で減圧、膨張して、低温低圧の気液二相冷媒となる。この気液二相冷媒は、中間熱交換器２３と給湯用熱源側熱交換器４４とに分かれて流れていく。 On the other hand, in the hot water supply refrigerant circuit 6, 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. At this time, in the hot water supply circuit 9, 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. Then, 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.

　中間熱交換器２３を流れた気液二相冷媒は、空調用冷媒から吸熱して蒸発し、低圧のガス冷媒となる。つまり、中間熱交換器２３内において、空調用冷媒と給湯用冷媒とによる熱交換が行われるのである。また、給湯用熱源側熱交換器４４を流れた気液二相冷媒も、大気から吸熱して蒸発し、低圧のガス冷媒となる。 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.

　この低圧のガス冷媒は、給湯用圧縮機４１の吸込口４１ａに流入し、給湯用圧縮機４１により再び圧縮されて高温高圧のガス冷媒となる。この運転モードでは、給湯用冷媒回路６における中間熱交換器２３は、空調用冷媒回路５を自然循環する空調用冷媒の熱を利用した蒸発器として機能することとなる。 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. In this operation mode, 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.

　この運転モードＮｏ．４－２では、空調用圧縮機２１を運転することなく、空調用冷媒を自然循環させて、住宅６０内を冷房できるので、消費電力を大幅に低減できる。 This operation mode No. In 4-2, since the air conditioning refrigerant can be naturally circulated and the house 60 can be cooled without operating the air conditioning compressor 21, power consumption can be significantly reduced.

　ここで、住宅６０内を効率よく冷房するためには、空調用冷媒の自然循環が連続して行われていかなければならないが、外気温度と住宅６０内の温度（室内温度）との差が小さい場合には、冷媒の密度差が小さくなり、自然循環による運転を安定して行うことが難しくなってしまう。しかし、運転モードＮｏ．４－２では、給湯用冷媒回路６による給湯運転が行われているため、中間熱交換器２３内に滞留している空調用冷媒は、中間熱交換器２３内を流れる給湯用冷媒によって強制的に熱を奪われるため、凝縮して液化し易くなる。つまり、給湯運転で得た給湯用冷媒の熱（冷熱）により、空調用冷媒の自然循環がアシストされるのである。そのため、空調用冷媒の自然循環による冷房の効率は良くなり、住宅６０内は快適なものとなる。 Here, in order to efficiently cool the inside of the house 60, natural circulation of the air conditioning refrigerant must be performed continuously, but the difference between the outside air temperature and the temperature inside the house 60 (room temperature) is When it is small, the density difference of the refrigerant becomes small, and it becomes difficult to stably operate by natural circulation. However, the operation mode No. In 4-2, since the hot water supply operation by the hot water supply refrigerant circuit 6 is performed, the air conditioning refrigerant accumulated in the intermediate heat exchanger 23 is forced by the hot water supply refrigerant flowing in the intermediate heat exchanger 23. Because it takes heat away, it becomes easy to condense and liquefy. That is, 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.

　また、外気温度が住宅６０内の露点温度以上である場合には、空調用冷媒を大気と熱交換させて空調冷媒回路５内を自然循環させるのみでは、住宅６０内の空気を冷却除湿することは不可能である。しかしながら、運転モードＮｏ．４－２では、給湯用膨張弁４３の弁開度を調整して、中間熱交換器２３を流れる給湯用冷媒の温度を任意に調整できるので、中間熱交換器２３を介して熱交換される空調用冷媒回路５内の空調用冷媒の温度を所望の温度（住宅６０内の露点温度以下となる温度）に調整することができる。よって、外気温度が住宅６０内の露点温度以上の環境下においても、住宅６０内の空気を自然循環サイクルによって冷却除湿することができるのである。 Further, when the outside air temperature is equal to or higher than the dew point temperature in the house 60, 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. However, 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.

　「運転モードＮｏ．５＜外気利用自然循環運転＞」（図８参照）
　運転モードＮｏ．５は、給湯用冷媒回路６による給湯運転を行いながら、外気を利用して空調用冷媒回路５内の空調用冷媒を自然循環させて冷房運転を行う運転モードである。この運転モードＮｏ．５では、中間熱交換器２３を用いないため、二方弁３５ａ、３５ｂ、４９ｂを閉じて、空調用冷媒および給湯用冷媒が中間熱交換器２３内を流れないようにしている。 "Driving mode No. 5 <Natural air using natural circulation operation>" (see Figure 8)
Operation mode No. Reference numeral 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. This operation mode No. In 5, since the intermediate heat exchanger 23 is not used, the two-way valves 35a, 35b, 49b are closed so that the air conditioning refrigerant and the hot water supply refrigerant do not flow in the intermediate heat exchanger 23.

　この運転モードＮｏ．５では、空調用圧縮機２１が停止しており、空調用圧縮機２１の前後の三方弁３４ａ、３４ｂにより、空調用圧縮機２１をバイパスする第２の空調用冷媒分岐路５ｃが開放され、空調用圧縮機２１を経由する経路（図８において点線で示す経路）が閉鎖されている。そのため、空調用冷媒は、空調用圧縮機２１をバイパスして空調用冷媒回路５内を循環する。なお、空調用膨張弁２７は、空調用利用側熱交換器２８で得たい交換熱量に応じて所定の開度に調整されている。 This operation mode No. At 5, the air conditioning compressor 21 is stopped, and the second air conditioning refrigerant branch path 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. A path (path indicated by a dotted line in FIG. 8) 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.

　空調用熱源側熱交換器２４内に滞留している空調用冷媒は、外気へ放熱して凝縮し、液化する。密度の大きい液冷媒は、重力の影響を受けて下降していき、空調用膨張弁２７を通り、空調用利用側熱交換器２８を流れる間に空調用冷温水循環回路８内を循環する冷水から吸熱して蒸発し、ガス化する。このとき、冷媒の密度差による圧力勾配ができるため、蒸発した冷媒は、空調用熱源側熱交換器２４に向かって流れていく。このように、空調用冷媒回路５は、空調用冷媒が自然循環する自然循環サイクルが形成されているのである。 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. At this time, since the pressure gradient can be generated by the difference in density of the refrigerant, the evaporated refrigerant flows toward the heat source side heat exchanger 24 for air conditioning. As described above, the air conditioning refrigerant circuit 5 is formed with a natural circulation cycle in which the air conditioning refrigerant naturally circulates.

　空調用冷温水循環回路８では、空調用利用側熱交換器２８を流れる空調用冷媒に放熱した冷水は、空調用冷温水循環ポンプ５２を駆動することにより、空調用冷温水配管を通って、室内熱交換器６１に流入する。室内熱交換器６１では、空調用冷温水循環回路８内の冷水と、住宅６０内の高温の空気とで熱交換が行われ、住宅６０の空気が冷却される。つまり、住宅６０の室内が冷房されることとなる。このとき、室内熱交換器６１を流れる冷水は、住宅６０内の空気から吸熱して昇温される。この昇温された冷水は、空調用冷温水循環ポンプ５２により空調用冷温水循環回路８内を循環し、再び空調用利用側熱交換器２８を流れる間に空調用冷媒回路５と熱交換を行って、所定温度まで冷却される。 In the air conditioning cold and hot water circulation circuit 8, 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. In 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.

　一方、給湯用冷媒回路６では、給湯用圧縮機４１で圧縮され高温高圧となったガス冷媒は、給湯用利用側熱交換器４２に流入する。給湯用利用側熱交換器４２内を流れる高温高圧のガス冷媒は、給湯回路９内を流れる水へ放熱して凝縮し、液化する。このとき、給湯回路９では、給湯用利用側熱交換器４２で給湯用冷媒回路６から温熱を受け取ることにより、供給された水が所定温度の湯となる。そして、液化した高圧の冷媒は、給湯用膨張弁４３で減圧、膨張して、低温低圧の気液二相冷媒となる。この気液二相冷媒は、給湯用熱源側熱交換器４４へ流れていき、大気から吸熱して蒸発し、低圧のガス冷媒となる。この低圧のガス冷媒は、給湯用圧縮機４１の吸込口４１ａに流入し、給湯用圧縮機４１により再び圧縮されて高温高圧のガス冷媒となる。 On the other hand, in the hot water supply refrigerant circuit 6, 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. At this time, in the hot water supply circuit 9, 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. Then, 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.

　この運転モードＮｏ．５では、空調用圧縮機２１を運転することなく、空調用冷媒を自然循環させて、住宅６０内を冷房できるので、消費電力を大幅に低減できる。 This operation mode No. In 5, since the air conditioning refrigerant can be naturally circulated and the house 60 can be cooled without operating the air conditioning compressor 21, power consumption can be significantly reduced.

　次に、制御装置１ａが行う空調給湯システムの制御について図９を用いて説明する。制御装置１ａは、リモコンからの指令信号、温度センサＴＥ１～ＴＥ８の検知信号、外気温度センサの検知信号などの入力信号に基づいて算出された結果が、上記した各種運転モードＮｏ．１～Ｎｏ．５のそれぞれに予め設定された運転モードの選択条件の何れを満たすかを判定し、その判定結果に応じた運転モードを選択して運転を行うように制御している。 Next, control of the air conditioning and hot water supply system performed by the control device 1a will be described with reference to FIG. 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.

　この第１の実施の形態例では、運転モードを選択するために必要なパラメータとして、設定室温(Tr_st)、設定湿度(Hr_st)、外気温度(Toa)、冷水入口温度(Twbi)、冷水出口設定温度(Twb_st)、給湯出力(Qhw)、給水温度(Twhi)、出湯温度(Twho)が用いられる。 In this first embodiment, as parameters necessary for selecting the operation mode, 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.

　設定室温(Tr_st)は、利用者がリモコンなどで設定する室内温度である。 The set room temperature (Tr_st) is the room temperature set by the user using a remote control or the like.

　設定湿度(Hr_st)は、利用者がリモコンなどで設定する室内湿度である。 The set humidity (Hr_st) is room humidity set by the user using a remote control or the like.

　外気温度(Toa)は、室外機で計測される外気の温度である。 The outside air temperature (Toa) is the temperature of the outside air measured by the outdoor unit.

　冷水入口温度(Twbi)は、冷温水系統で測定される温度であり、具体的には、空調用冷温水循環回路８の温度センサＴＥ１で測定される温度である。 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.

　冷水出口設定温度(Twb_st)は、設定室温(Tr_st)と設定湿度(Hr_st)と冷水入口温度(Twbi)とに基づき制御装置１ａが決定する温度である。 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).

　給湯出力(Qhw)は、利用者要求と給水温度(Twhi)から制御装置１ａが決定する値である。 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).

　給水温度(Twhi)は、熱源機給湯系統で測定される温度であり、具体的には、温度センサＴＥ７で測定される温度である。 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.

　出湯温度(Twho)は、給湯利用側出口温度（温度センサＴＥ８で測定される温度）の設定値と利用者の要求と空調給湯システム側の仕様とに基づいて決定される温度である。 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.

　制御装置１ａは、所定のタイミングで、入力信号に基づき、（ａ）利用側要求、（ｂ）給湯機運転可否の条件、（ｃ）設定室温Tr_st－関数ｆ１（設定室温Tr_st，設定湿度Hr_st）と外気温度Toaとの差、（ｄ）設定室温Tr_st－関数ｆ２（Tr_st，Hr_st）と外気温度Toaとの差、（ｅ）冷水出口設定温度Twb_stと冷水入口温度Twbiの差、（ｆ）圧縮機運転時間に関する制限、（ｇ）吸熱量－排熱量、即ち、関数ｆ３（Twb_st，Twbi，Toa）－関数ｆ４（Qhw，Twhi，Twho，Toa）を求める。そして、上記（ａ）～（ｇ）の結果に応じて、制御装置１ａは、運転パターンＮｏ．１～Ｎｏ．５の何れかを決定する。 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 | running pattern No. 1 to No. Decide on one of five.

　例えば、図９の示すように、（ａ）が「冷房運転」、（ｂ）が「利用者の要求＝無」、（ｃ）が「＜０」、（ｄ）が「＜０」、（ｅ）が「＞０」の場合には、制御装置１ａは、運転モードＮｏ．１を選択する。また、（ａ）が「冷房運転」、（ｂ）が「利用者の要求＝有」、（ｃ）が「＜０」、（ｄ）が「＞０」、（ｅ）が「ΔＴ３＜」かつ「＜ΔＴ６」、（ｆ）が「空調用圧縮機２１停止、または圧縮機２台運転から所定時間Time2経過後」、（ｇ）が「＜０」の場合には、制御装置１ａは、運転モードＮｏ．４－１を選択する。このようにして、制御装置１ａは、条件に応じて好適な運転モードを選択している。また、（ａ）が「暖房運転」の場合、（ｂ）～（ｇ）とは関係なく運転モードＮｏ．３を選択する。なお、図９において、Time1、Time2、Time3、ΔＴ３、ΔＴ４、ΔＴ６は、空調給湯システムの仕様などに応じて予め定められた値である。 For example, as shown in FIG. 9, (a) is “cooling operation”, (b) is “user request = no”, (c) is “<0”, (d) is “<0”, When e) is “> 0”, the control device 1a sets the operation mode No. Select 1 In addition, (a) is “cooling operation”, (b) is “user request = yes”, (c) is “<0”, (d) is “> 0”, and (e) is “ΔT3 <” And “<ΔT6”, (f) “after a predetermined time 2 has elapsed from the operation of the air conditioning compressor 21 stop or two compressors operation”, (g) is “<0”, the controller 1a is Operation mode No. Select 4-1. Thus, 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, ΔT3, ΔT4, and ΔT6 are values determined in advance according to the specification of the air conditioning and hot water supply system.

　なお、実際に運転モードを切り替える場合は、冷房負荷が時々刻々と変動するため（圧縮機２台－圧縮機１台）の入力差＝０を切替点とせず、入力差＞ｘ１（ｘ１＞０）で給湯側のみ運転、入力差＜ｘ２（ｘ２＜０）で両サイクル圧縮式運転として切り替えると、運転モードの切り替えが頻繁に生じることを回避できる。 In addition, when switching the operation mode, 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.

　次に、空調用冷媒回路５を圧縮式サイクルとして用いた運転モードＮｏ．１、Ｎｏ．２－１、Ｎｏ．２－２、Ｎｏ．３における空調用圧縮機２１の回転数の制御、空調用膨張弁２７の弁開度の制御、および空調用熱源側熱交換器２４のファンの回転数の制御について説明する。これらの制御は、制御装置１ａによって行われている。 Next, in the operation mode No. 1 in which the air conditioning refrigerant circuit 5 is used as a compression type cycle. 1, No. 2-1, No. 2-2, no. The control of the rotational speed of the air conditioning compressor 21, the control of the valve opening degree of the air conditioning expansion valve 27, and the control of the rotational speed of the fan of the air conditioning heat source side heat exchanger 24 in 3 will be described. These controls are performed by the control device 1a.

　空調用熱源側熱交換器２４のファンは、通常は一定の回転数に制御されている。 The fan of the air conditioning heat source side heat exchanger 24 is usually controlled to have a constant rotational speed.

　空調用圧縮機２１の回転数制御は、空調用冷温水循環回路８内を循環する水の空調用利用側熱交換器２８の出口温度と目標温度（利用者によって設定された室内設定温度に応じて定まる値）の偏差に基づいて行われる。なお、水の空調用利用側熱交換器２８の出口温度は、冷房運転では、温度センサＴＥ２で測定された値であり、暖房運転では、温度センサＴＥ１で測定された値である。制御装置１ａは、冷房運転において「目標温度－出口温度＞０」であれば空調用圧縮機２１の回転数を減速にし、「目標温度－出口温度＜０」であれば、空調用圧縮機２１の回転数を増速にする。暖房運転における制御も冷房運転と同様であり、「目標温度－出口温度＞０」であれば空調用圧縮機２１の回転数を増速にし、「目標温度－出口温度＜０」であれば、空調用圧縮機２１の回転数を減速にする。 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.

　空調用膨張弁２７の弁開度の制御は、空調用圧縮機２１の吸込温度（温度センサＴＥ３で測定された値）、空調用圧縮機２１の回転数、および吸熱源温度に基づき行われる。具体的には、制御装置１ａは、空調用圧縮機２１の吸込における低圧冷媒ガスの過熱度が所定の温度になるように、空調用圧縮機２１の回転数、吸熱源温度に基づき決定された吸込温度の目標値と実測値との偏差から膨張弁開度の変化量を決め、空調用膨張弁２７を開動作（＋パルス）あるいは閉動作（－パルス）させる。ここで，吸熱源温度として、暖房運転では「外気温度」が用いられ、冷房運転では「空調用冷温水循環回路８内を流れる冷水の空調用利用側熱交換器２８の入口温度、即ち、ＴＥ１で測定された温度」が用いられる。吸込温度の目標値の算出は、予め定められた関数を用いても良いし、空調用圧縮機２１の吸込温度、空調用圧縮機２１の回転数、および吸熱源温度と吸込温度の目標値とが予め対応付けられたテーブルを用いても良い。なお、空調用圧縮機２１の吸込温度に代えて吐出温度（温度センサＴＥ４で測定された値）により制御を行っても良く、吐出温度を用いた場合には、外乱に対して制御目標とする温度が安定して計測される利点がある。 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). Here, 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. When the discharge temperature is used, the control target is set for disturbance There is an advantage that the temperature is measured stably.

　次に、給湯用冷媒回路６を圧縮式サイクルとして用いた運転モードＮｏ．１、Ｎｏ．２－１、Ｎｏ．２－２、Ｎｏ．３、Ｎｏ．４－１、Ｎｏ．４－２、およびＮｏ．５における給湯用圧縮機４１の回転数の制御、給湯用膨張弁４３の弁開度の制御、給湯用熱源側熱交換器４４のファンの回転数、および給湯流量の制御は、制御装置１ａによって以下のように行われている。 Next, in the operation mode No. 1 using the hot water supply refrigerant circuit 6 as a compression type cycle. 1, No. 2-1, No. 2-2, no. 3, No. 4-1, No. 4-2, and no. Control of the rotational speed of the hot water supply compressor 41, control of the valve opening degree of the hot water supply expansion valve 43, control of the rotational speed of the fan of the hot water supply heat source side heat exchanger 44, and control of the hot water supply flow rate It is done as follows.

　給湯用熱源側熱交換器４４のファンは、通常は一定の回転数に制御されている。 The fan of the heat source side heat exchanger 44 for hot water supply is usually controlled to have a constant rotational speed.

　給湯流量は、給湯回路９を流れる水の給水温度（温度センサＴＥ７で測定された値）あるいは給湯回路９の給湯負荷側の機器（浴槽など）からの要求に応じて制御される。 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.

　給湯用圧縮機４１の回転数制御は、給湯回路９に給水される水の給水温度（温度センサＴＥ８で測定された値）と、浴槽へ供給する温水（給湯用利用側熱交換器４２の下流を流れる温水）の目標温度（利用者によって設定された給湯設定温度を考慮して定まる値）との偏差に応じて行われる。具体的には、制御装置１ａは、給湯運転において「目標温度－給湯温度＞０」であれば給湯用圧縮機４１の回転数を増速にし、「目標温度－給湯温度＜０」であれば、給湯用圧縮機４１の回転数を減速にする。 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.

　給湯用膨張弁４３の弁開度の制御は、給湯用圧縮機４１の吸込温度（温度センサＴＥ５で測定された値）、給湯用圧縮機４１の回転数、および吸熱源温度に基づき行われる。具体的には、制御装置１ａは、給湯用圧縮機４１の吸込における低圧冷媒ガスの過熱度が所定の温度になるように、給湯用圧縮機４１の回転数、吸熱源温度に基づき決定された吸込温度の目標値と実測値との偏差から膨張弁開度の変化量を決め、給湯用膨張弁４３を開動作（＋パルス）あるいは閉動作（－パルス）させる。ここで、吸熱源温度には「外気温度」が用いられる。吸込温度の目標値の算出は、予め定められた関数を用いても良いし、給湯用圧縮機４１の吸込温度、給湯用圧縮機４１の回転数、および吸熱源温度と吸込温度の目標値とが予め対応付けられたテーブルを用いても良い。なお、給湯用圧縮機４１の吸込温度に代えて吐出温度（温度センサＴＥ６で測定された値）により制御を行っても良く、吐出温度を用いた場合には、外乱に対して制御目標とする温度が安定して計測される利点がある。 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). Here, 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. Note that 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. When the discharge temperature is used, the control target is set against disturbances There is an advantage that the temperature is measured stably.

　次に、空調用冷媒回路５を自然循環式サイクルとして用いた運転モードＮｏ．４－１、Ｎｏ．４－２における給湯用圧縮機４１の回転数の制御、給湯用膨張弁４３の弁開度の制御、給湯流量の制御、および空調用膨張弁２７の弁開度の制御は、制御装置１ａによって以下のように行われている。 Next, in the operation mode No. 4 in which the air conditioning refrigerant circuit 5 is used as a natural circulation type cycle. 4-1, No. The control of the rotational speed of the hot water supply compressor 41, the control of the valve opening degree of the hot water supply expansion valve 43, the control of the hot water supply flow rate, and the control of the valve open degree of the air conditioning expansion valve 27 in 4-2 are performed by the controller 1a. It is done as follows.

　（ａ１）給湯を主に利用した運転の場合（給湯出力を固定した場合）
　次に説明する制御は、例えば、住宅６０の室内にエアコン等の補助空調機が併設しているような場合に用いると良い。 (A1) In the case of operation mainly using hot water supply (when the hot water supply output is fixed)
The control to be described next may be used, for example, when an auxiliary air conditioner such as an air conditioner is juxtaposed in the room of the house 60.

　給湯流量は、給湯回路９を流れる水の給水温度（温度センサＴＥ７で測定された値）と給湯温度（給湯用利用側熱交換器４２の下流側を流れる温水の温度）の目標値から定まる目標流量に応じて制御される。なお、給水温度と給湯温度の目標値とを比較して、給湯流量を増減するように制御しても良い。 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.

　給湯用圧縮機４１の回転数制御は、給湯回路９における給湯用利用側熱交換器４２の出口温度、即ち、給湯出口温度（温度センサＴＥ８で測定された値）と、給湯の目標温度（利用者からの要求やシステムの仕様によって定まる値）との偏差に応じて行われる。具体的には、制御装置１ａは、「給湯目標温度－給湯出口温度＜０」であれば給湯用圧縮機４１の回転数を減速にし、「給湯目標温度－給湯出口温度＞０」であれば、給湯用圧縮機４１の回転数を増速にする。なお、給水温度と給湯の目標温度とに基づいて給湯用圧縮機４１の回転数制御を行っても良い。 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.

　給湯用膨張弁４３の弁開度の制御は、給湯用圧縮機４１の吸込温度（温度センサＴＥ５で測定された値）、空調用冷温水循環回路８内を循環する水の空調用利用側熱交換器２８の出口温度（温度センサＴＥ２で測定された値）の目標値と空調用利用側熱交換器２８の入口温度（温度センサＴＥ１で測定された値）、および給湯用圧縮機４１の回転数から定まる弁開度の目標値と、弁開度の実測値とに基づいて制御される。具体的には、制御装置１ａは、「弁開度の目標値－弁開度の実測値＞０」であれば給湯用膨張弁４３の弁開度を開動作（＋パルス）させ、「弁開度の目標値－弁開度の実測値＜０」であれば給湯用膨張弁４３の弁開度を閉動作（－パルス）させる。ここで、弁開度の目標値の算出には、予め定められた関数を用いても良いし、給湯用圧縮機４１の吸込温度、空調用冷温水循環回路８内を循環する水の空調用利用側熱交換器２８の出口温度の目標値と空調用利用側熱交換器２８の入口温度、および給湯用圧縮機４１の回転数と弁開度の目標値とが予め対応付けられたテーブルを用いても良い。なお、給湯用圧縮機４１の吸込温度に代えて吐出温度（温度センサＴＥ６で測定された値）により制御を行っても良い。 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. Specifically, 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). Here, for calculation of the target value of the valve opening degree, 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 Using a table in which the target value of the outlet temperature of the side heat exchanger 28, the inlet temperature of the use-side heat exchanger for air conditioning 28, and the rotational speed of the hot water supply compressor 41 and the target value of the valve opening degree are associated beforehand It is good. 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.

　空調用膨張弁２７の弁開度の制御は、空調用冷温水循環回路８内を循環する水の空調用利用側熱交換器２８の目標出口温度と、実測した出口温度（温度センサＴＥ２で測定された値）との偏差に基づいて制御される。具体的には、制御装置１ａは、「目標出口温度－実測した出口温度＜０」であれば空調用膨張弁２７の弁開度を開動作（＋パルス）させ、「目標出口温度－実測した出口温度＞０」であれば空調用膨張弁２７の弁開度を閉動作（－パルス）させる。 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).

　（ｂ１）空調を主に利用した運転の場合（給湯出力を変化させる場合）
　給湯回路９から供給する給湯流量は、空調用冷温水循環回路８内を循環する水の空調用利用側熱交換器２８の目標出口温度と、実測した入口温度（温度センサＴＥ１で測定された値）との偏差に応じて制御される。具体的には、制御装置１ａは、「目標入口温度－実測した入口温度＜０」であれば給湯流量を増加させ、「目標入口温度－実測した入口温度＞０」であれば、給湯流量を減少させる。 (B1) In the case of operation mainly using air conditioning (when changing the hot water supply output)
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.

　給湯用圧縮機４１の回転数制御は、給湯回路９における給湯用利用側熱交換器４２の出口温度、即ち、給湯出口温度（温度センサＴＥ８で測定された値）と、給湯の目標温度（利用者によって設定された給湯設定温度を考慮して定まる値）との偏差に応じて行われる。具体的には、制御装置１ａは、「給湯目標温度－給湯出口温度＜０」であれば給湯用圧縮機４１の回転数を減速にし、「給湯目標温度－給湯出口温度＞０」であれば、給湯用圧縮機４１の回転数を増速にする。なお、給水温度と給湯の目標温度とに基づいて給湯用圧縮機４１の回転数制御を行っても良い。 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.

　給湯用膨張弁４３の弁開度の制御は、給湯用圧縮機４１の吸込温度（温度センサＴＥ５で測定された値）、空調用冷温水循環回路８内を循環する水の空調用利用側熱交換器２８の出口温度（温度センサＴＥ２で測定された値）の目標値と空調用利用側熱交換器２８の入口温度（温度センサＴＥ１で測定された値）、および給湯用圧縮機４１の回転数から定まる弁開度の目標値と、弁開度の実測値とに基づいて制御される。具体的には、制御装置１ａは、「弁開度の目標値－弁開度の実測値＞０」であれば給湯用膨張弁４３の弁開度を開動作（＋パルス）させ、「弁開度の目標値－弁開度の実測値＜０」であれば給湯用膨張弁４３の弁開度を閉動作（－パルス）させる。ここで、弁開度の目標値の算出には、予め定められた関数を用いても良いし、給湯用圧縮機４１の吸込温度、空調用冷温水循環回路８内を循環する水の空調用利用側熱交換器２８の出口温度の目標値と空調用利用側熱交換器２８の入口温度、および給湯用圧縮機４１の回転数と弁開度の目標値とが予め対応付けられたテーブルを用いても良い。なお、給湯用圧縮機４１の吸込温度に代えて吐出温度（温度センサＴＥ６で測定された値）により制御を行っても良い。 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. Specifically, 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). Here, for calculation of the target value of the valve opening degree, 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 Using a table in which the target value of the outlet temperature of the side heat exchanger 28, the inlet temperature of the use-side heat exchanger for air conditioning 28, and the rotational speed of the hot water supply compressor 41 and the target value of the valve opening degree are associated beforehand It is good. 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.

　空調用膨張弁２７の弁開度の制御は、空調用冷温水循環回路８内を循環する水の空調用利用側熱交換器２８の目標出口温度と、実測した出口温度（温度センサＴＥ２で測定された値）との偏差に基づいて制御される。具体的には、制御装置１ａは、「目標出口温度－実測した出口温度＜０」であれば空調用膨張弁２７の弁開度を開動作（＋パルス）させ、「目標出口温度－実測した出口温度＞０」であれば空調用膨張弁２７の弁開度を閉動作（－パルス）させる。 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).

　なお、自然循環式サイクルの空調排熱が給湯サイクルの吸熱量に対して不足する場合には、制御装置１ａは、給湯用冷媒回路６における給湯用熱源側熱交換器４４の上流の二方弁４９ａを開き、給湯用熱源側熱交換器４４のファンを動作させる。これにより、給湯量冷媒回路６を流れる給湯用冷媒は、給湯用熱源側熱交換器４４を介して外気から吸熱を行うことが可能となる。よって、給湯サイクルが必要とする吸熱量のうち空調側の自然循環式サイクルからの吸熱では賄えなかった不足分を、外気からの吸熱で補うことができる。吸熱量の不足は、給湯回路９における給水温度（温度センサＴＥ７で測定された温度）、給水流量あるいは給湯用圧縮機４１の回転数から推定される吸熱量と、空調用冷温水循環回路８における空調用利用側熱交換器２８の冷水入口温度（温度センサＴＥ１で測定された温度）と冷水出口温度の目標値から推定される必要放熱量との差で判断することができる。 When the air conditioning exhaust heat of the natural circulation type cycle is insufficient with respect to the heat absorption amount of the hot water supply cycle, 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. As a result, 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.

　また、給湯サイクルの吸熱量に対し自然循環式サイクルの空調排熱が過剰な場合には、制御装置１ａは、空調用冷媒回路５における空調用熱源側熱交換器２４の前後の二方弁３５ｃ、３５ｄを開き、空調用熱源側熱交換器２４のファンを動作させる。これにより、空調用冷媒回路５を自然循環する空調用冷媒は、空調用熱源側熱交換器２４を介して外気へ放熱を行うことが可能となる。よって、自然循環式サイクルの空調排熱のうち給湯サイクルへ放熱して残った空調排熱、即ち、空調排熱の過剰分を、外気へ放熱することができる。排熱過剰は、給湯回路９における給水温度（温度センサＴＥ７で測定された温度）、給水流量あるいは給湯用圧縮機４１の回転数から推定される吸熱量と、空調用冷温水循環回路８における空調用利用側熱交換器２８の冷水入口温度（温度センサＴＥ１で測定された温度）と冷水出口温度の目標値から推定される必要放熱量との差で判断することができる。 Further, when the air conditioning exhaust heat of the natural circulation type cycle is excessive with respect to the heat absorption amount of the hot water supply cycle, 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. Thus, 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.

　次に、本発明の第１の実施の形態例に係る空調給湯システムの効果について、図１０を参照しながら説明する。図１０（ａ）は本発明の第１の実施の形態例に係る空調給湯システムの冷媒の圧力－エンタルピ線図であり、図１０（ｂ）は、従来の空調給湯システムの冷媒の圧力－エンタルピ線図である。 Next, the effects of the air conditioning and hot water supply system according to the first embodiment of the present invention will be described with reference to FIG. 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, and FIG. 10 (b) is a pressure of the refrigerant of the conventional air conditioning and hot water supply system-enthalpy FIG.

　従来の空調給湯システムにおける冷房／給湯運転では、冷房時に空調用冷媒回路５を圧縮式サイクルで運転し、同時に、給湯用冷媒回路６を圧縮式サイクルで運転するため、図１０（ｂ）に示すように、空調側の圧縮式サイクルは、ＰＡ１’→ＰＡ２’→ＰＡ３’→ＰＡ４’の循環経路で動作し、給湯側の圧縮式サイクルは、ＰＨ１’→ＰＨ２’→ＰＨ３’→ＰＨ４’の循環経路で動作する。ここで、ＰＡ１’は空調用圧縮機２１の吸込口２１ａの空調用冷媒の状態、ＰＡ２’は空調用圧縮機２１の吐出口２１ｂの空調用冷媒の状態、ＰＡ３’は中間熱交換器２３の出口の空調用冷媒の状態、ＰＡ４’は空調用利用側熱交換器２８の入口の空調用冷媒の状態である。また、ＰＨ１’は給湯用圧縮機４１の吸込口４１ａの給湯用冷媒の状態、ＰＨ２’は給湯用圧縮機４１の吐出口４１ｂの給湯用冷媒の状態、ＰＨ３’は給湯用利用側熱交換器４２の出口の給湯用冷媒の状態、ＰＨ４’は中間熱交換器２３の入口の給湯用冷媒の状態である。 In the cooling / hot water supply operation in the conventional air conditioning and hot water supply system, 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. Thus, the compression type cycle on the air conditioning side operates in the circulation path of PA1 ′ → PA2 ′ → PA3 ′ → PA4 ′, and the compression type cycle on the hot water supply side is a circulation of PH1 ′ → PH2 ′ → PH3 ′ → PH4 ′ Work on the path. Here, 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, and 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. Further, 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, and PH3 'is the use side heat exchanger for hot water supply The state of the hot water supply refrigerant at the outlet of 42, PH4 'is the state of the hot water supply refrigerant at the inlet of the intermediate heat exchanger 23.

　この図１０（ｂ）から明らかなように、冷房時に空調側と給湯側を共に圧縮式サイクルで運転した場合には、空調用圧縮機２１による圧縮仕事ＷＡ’と給湯用圧縮機４１による圧縮仕事ＷＨ’とを合計した仕事量Ｗが発生する。即ち、仕事量Ｗ＝ＷＡ’＋ＷＨ’である。 As is clear from FIG. 10 (b), when both the air conditioning side and the hot water supply side are operated in the compression type cycle during cooling, the compression work by the air conditioning compressor 21 and the compression work by the hot water supply compressor 41 An amount of work W obtained by totaling WH 'is generated. That is, the amount of work W = WA '+ WH'.

　これに対して、冷房時に空調用冷媒回路５を自然循環式サイクルにて運転し、同時に、給湯用冷媒回路６を圧縮式サイクルで運転した場合（例えば、運転モードＮｏ．４－１、Ｎｏ．４－２）には、図１０（ａ）に示すように、空調側の自然循環式サイクルは、ＰＡ１→ＰＡ２→ＰＡ３の循環経路で動作し、給湯側の圧縮式サイクルは、ＰＨ１→ＰＨ２→ＰＨ３→ＰＨ４の循環経路で動作する。ここで、ＰＡ１は中間熱交換器２３の出口の空調用冷媒の状態、ＰＡ２は空調用利用側交換器２８の入口の空調用冷媒の状態、ＰＡ３は中間熱交換器２３の入口の空調用冷媒の状態である。また、ＰＨ１は給湯用圧縮機４１の吸込口４１ａの給湯用冷媒の状態、ＰＨ２は給湯用圧縮機４１の吐出口４１ｂの給湯用冷媒の状態、ＰＨ３は給湯用利用側熱交換器４２の出口の給湯用冷媒の状態、ＰＨ４は中間熱交換器２３の入口の給湯用冷媒の状態である。 On the other hand, when 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. Here, 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, and PA3 is the air conditioning refrigerant at the inlet of the intermediate heat exchanger 23. It is in the state of In addition, 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, and 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.

　この図１０（ａ）から明らかなように、冷房時に空調側を自然循環式サイクルで運転し、給湯側を圧縮式サイクルで運転した場合には、前述したように給湯側の圧縮式サイクルの運転により、空調側の自然循環式サイクルをアシストするため、給湯用圧縮機４１による圧縮仕事ＷＨは上記の圧縮仕事ＷＨ’より増えるものの、空調用圧縮機２１による圧縮仕事ＷＡ’が不要となるため、空調側を自然循環式サイクルで運転し給湯側を圧縮式サイクルで運転した場合の仕事量Ｗ＝ＷＨとなる。この圧縮仕事ＷＨは、圧縮仕事ＷＡ’と圧縮仕事ＷＨ’の合計値よりも小さい。即ち、ＷＨ＜ＷＡ’＋ＷＨ’の関係が成り立つ。 As apparent from FIG. 10 (a), when the air conditioning side is operated at the natural circulation type cycle at the time of cooling and the hot water supply side is operated at the compression type cycle, the operation of the compression type cycle on the hot water side as described above. Thus, although the compression work WH by the hot water supply compressor 41 is larger than the above compression work WH ′ in order to assist the natural circulation type cycle on the air conditioning side, the compression work WA ′ by the air conditioning compressor 21 becomes unnecessary. The workload W = WH when the air conditioning side is operated by the natural circulation type cycle and the hot water supply side is operated by the compression type cycle. The compression work WH is smaller than the sum of the compression work WA 'and the compression work WH'. That is, the relationship of WH <WA '+ WH' is established.

　このように、空調側を自然循環式サイクルによる運転にした場合、空調給湯システム全体としてＷＡ’＋ＷＨ’－ＷＨで求められる圧縮仕事の分だけ仕事量を軽減することができる。つまり、第１の実施の形態例に係る空調給湯システムによれば、空調側の自然循環式サイクルと給湯サイクルとを組み合わせた運転モードによって、運転効率を高め、省エネに寄与するとともに、消費電力の大幅な低減を実現できるのである。 As described above, when the air conditioning side is operated by the natural circulation type cycle, it is possible to reduce the workload by the amount of the compression work obtained by WA '+ WH'-WH as the whole air conditioning and hot water supply system. That is, according to the air-conditioning and hot-water supply system according to the first embodiment, 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.

　［本発明の第２の実施形態］
　次に、本発明の第２の実施の形態例に係る空調給湯システムについて図１１を用いて説明するが、第１の実施の形態例に係る空調給湯システムと同一の構成については、同一の符号を付して、その説明を省略する。第２の実施の形態例に係る空調給湯システムは、第１の実施の形態例に係る空調給湯システムに比べて、給湯回路９に蓄熱・貯湯ユニット７を設けた点に相違がある。この相違について、以下、詳しく説明していくことにする。 Second Embodiment of the Present Invention
Next, 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.

　蓄熱・貯湯ユニット７は、貯湯タンク７０と蓄熱タンク７１とを備えて構成されており、貯湯タンク７０および蓄熱タンク７１は、給湯用回路９を構成する給湯用配管７２、７３とそれぞれ配管を用いて接続されている。貯湯タンク７０は、蓄熱が可能であって、給湯用冷媒回路６と熱交換して生成された温水を貯めるためのタンクである。一方、蓄熱タンク７１は、蓄熱が可能なタンクであって、太陽熱集熱器７４で集熱された熱が取り込まれるようになっている。この蓄熱タンク７１内の水は、太陽熱集熱器７４により冷水と温水の間の温度（中間温度）に温められる。給湯回路９内の水は、給湯用循環ポンプを駆動することにより、図９の矢印の方向に流れていき、給湯用利用側熱交換器４２にて給湯用冷媒と熱交換を行って温水となり、貯留タンク７０へ流れていく。 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. On the other hand, 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.

　貯湯タンク７０から給湯負荷側の機器へ温水を供給する配管と、蓄熱タンク５０から給湯負荷側である浴槽へ中間温度の水を供給する配管とは、蓄熱・貯湯ユニット７内で合流されており、配管と配管の合流部分には、図示しない三方弁が設けられている。また、給湯負荷側の機器に接続される配管には、図示しない給湯供給ポンプが設けられている。このように構成された蓄熱・貯湯ユニット７によれば、制御装置１ａにより上記三方弁を操作することにより、貯湯タンク７０内の温水と、蓄熱タンク５０内の中間温度の水とを混ぜて好適な温度の温水を浴槽等へ供給できることとなる。 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. Moreover, 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. According to the heat storage and hot water storage unit 7 configured as described above, it is preferable to mix the hot water in the hot water storage tank 70 and the water at the intermediate temperature in the heat storage tank 50 by operating the three-way valve by the controller 1a. It is possible to supply warm water of a moderate temperature to a bath tub or the like.

　ところで、一般住宅において空調（冷房）負荷は、昼間から夕方にかけて生じるが、給湯需要は夜間に存在する。つまり、冷房運転が主に行われる時間帯と、給湯運転が主に行われる時間帯には異なっている（ズレがある）のが一般的である。ここで、蓄熱・貯湯ユニット７がない場合、例えば、給湯回路９と給湯負荷側の機器（浴槽など）とが直接接続されているような場合には、給湯需要の発生する夜間の時間帯にしか給湯サイクルと空調側の自然循環サイクルとを用いた運転モード（運転モードＮｏ．４－１、Ｎｏ．４－２）による運転を行うことができない。 By the way, although 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. Here, when there is no heat storage and hot water storage unit 7, for example, when 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.

　しかし、本発明の第２の実施の形態例に係る空調給湯システムでは、蓄熱・貯湯ユニット７を備えているので、任意の時間に蓄熱タンク５０と貯湯タンク７０に蓄えられた温水を供給することができる。もう少し詳しく説明すると、第２の実施の形態例では、給湯負荷がない場合であっても、給湯サイクルを運転しながら自然循環式サイクルによる空調を行いつつ、その給湯運転で得られた湯を蓄熱・貯湯ユニット７に蓄えておくことにより、必要なときに湯を使用することができるのである。よって、第２の実施の形態例に係る空調給湯システムは、自然循環式サイクルによる運転モードを活用し易くなり、空調給湯システムの消費電力を低減することができる。 However, in the air conditioning and hot water supply system according to the second embodiment of the present invention, 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.

　なお、貯湯タンク７０と蓄熱タンク７１の何れか一方のみを設けた構成であっても、熱を有効利用することができることは言うまでもない。また、太陽熱集熱器７４を貯湯タンク７０に組み込むようにしても良い。また、蓄熱タンク７１の水を中間熱交換器２３に導入し、この中間熱交換器２３において、空調用冷媒回路５の空調用冷媒と給湯用冷媒回路６の給湯用冷媒と、蓄熱タンク７１内の水（中間温度の水）との３流体間で熱交換を行うようにしても良い。かかる構成によれば、冷房運転による排熱をより一層有効に利用することができ、省エネ効果も高まる。 Needless to say, even if only one of the hot water storage tank 70 and the heat storage tank 71 is provided, heat can be effectively used. Also, the solar heat collector 74 may be incorporated into the hot water storage tank 70. Further, 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.

　［本発明の第３の実施形態］
　次に、本発明の第３の実施の形態例に係る空調給湯システムについて図１２を用いて説明するが、第１の実施の形態例に係る空調給湯システムと同一の構成については、同一の符号を付して、その説明を省略する。第３の実施の形態例に係る空調給湯システムは、空調用利用側熱交換器として、第１の空調用利用側分割熱交換器２８ａと第２の空調用利用側分割熱交換器２８ｂの２つの熱交換器に分割されている点、分岐点Ｄと分岐点Ｅとを繋ぐバイパス経路が形成されている点、および、分岐点Ｃと分岐点Ｆとを繋ぐバイパス経路が形成されている点が第１の実施の形態例に係る空調給湯システムに比べて、大きく相違している。この相違について、以下、詳しく説明していくことにする。 Third Embodiment of the Present Invention
Next, 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. In the air conditioning and hot water supply system according to the third embodiment, 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. A point divided into two heat exchangers, a point forming a bypass route connecting branch point D and branch point E, and a point forming a bypass route connecting branch point C and branch point F However, in comparison with the air-conditioning and hot-water supply system according to the first embodiment, there is a large difference. This difference will be described in detail below.

　第１の空調用利用側分割熱交換器２８ａおよび第２の空調用利用側分割熱交換器２８ｂは、何れも空調用冷媒回路５を流れる空調用冷媒と、空調用冷温水循環回路８内を流れる水とで熱交換が可能な構成となっており、第１の空調用利用側分割熱交換器２８ａと第２の空調用利用側分割熱交換器２８ｂとは直列に接続されている。なお、第１の空調用利用側分割熱交換器２８ａおよび第２の空調用利用側分割熱交換器２８ｂは、ヘッド差を設けるために、空調用熱源側熱交換器２４よりも低い位置に設置されている。 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.

　中間熱交換器２３と二方弁３５ｂの間に位置する分岐点Ｄと、第１の空調用利用側分割熱交換器２８ａと第２の空調用利用側分割熱交換器２８ｂとの間に位置する分岐点Ｅとは、第２の空調用冷媒バイパス配管２９ｂで接続されている。この第２の空調用冷媒バイパス配管２９ｂには、空調用補助膨張弁２７ｂが組み込まれている。 A position between a branch point D located between the intermediate heat exchanger 23 and the two-way valve 35b, and between the first air conditioning use side split heat exchanger 28a and the second air conditioning use side split heat exchanger 28b 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.

　空調用熱源側熱交換器２４と二方弁３５ｃとの間に位置する分岐点Ｃと、第１の空調用利用側分割熱交換器２８ａと第２の空調用利用側分割熱交換器２８ｂとの間に位置する分岐点Ｆとは、第３の空調用冷媒バイパス配管２９ｃで接続されている。この空調用冷媒バイパス配管２９ｂには、二方弁３５ｆが組み込まれている。さらに、分岐点Ｅと分岐点Ｆの間には、二方弁３５ｇが設けられている。 A branch point C located between the air conditioning heat source side heat exchanger 24 and the two-way valve 35c, a first air conditioning use side split heat exchanger 28a, and a second air conditioning use side split heat exchanger 28b 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.

　第３の実施の形態例に係る空調給湯システムでは、上記した構成の相違により、空調用冷媒が自然循環する経路を複数設定することができる。まず、第１の自然循環経路は、分岐点Ｂ→分岐点Ｉ→分岐点Ｄ→分岐点Ｅ→分岐点Ａ→分岐点Ｂを辿る経路である。この第１の自然循環経路では、中間熱交換器２３で給湯用冷媒回路６内を流れる給湯用冷媒と熱交換して液化した空調用冷媒は、密度差により自然に空調用冷媒バイパス配管２９ｂを流れていき、空調用補助膨張弁２７ｂを経由して第２の空調用利用側分割熱交換器２８ｂへと流入する。そして、液化した空調用冷媒は、第２の空調用利用側分割熱交換器２８ｂで空調用冷温水循環回路８内を流れる水から吸熱して蒸発し、自然に空調用冷媒バイパス配管２９を通って、中間熱交換器２３へと戻っていく。なお、この第１の自然循環経路が形成される際には、二方弁３５ｂ、二方弁３５ｃ、二方弁３５ｆは閉じており、空調用補助膨張弁２７ｂは、適度な弁開度に調整されている。 In the air conditioning and hot water supply system according to the third embodiment, a plurality of routes through which the air conditioning refrigerant naturally circulates can be set by the difference in the configuration described above. First, 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. In this first natural circulation path, 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. It flows and flows into the second air conditioning use side split heat exchanger 28b via the air conditioning auxiliary expansion valve 27b. Then, 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. When the first natural circulation path is formed, 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.

　次に、第２の自然循環経路は、分岐点Ｂ→分岐点Ｉ→分岐点Ｄ→分岐点Ｊ→分岐点Ｆ→分岐点Ｅ→分岐点Ａ→分岐点Ｂを辿る経路である。この第２の自然循環経路では、中間熱交換器２３で給湯用冷媒回路６内を流れる給湯用冷媒と熱交換して液化した空調用冷媒は、密度差により自然に空調用冷媒タンク２６へと流れていき、空調用膨張弁２７を経由して第１の空調用利用側熱交換器２８ａ、第２の空調用利用側分割熱交換器２８ｂの順に流れていく。液化した空調用冷媒は、第１の空調用利用側熱交換器２８ａおよび第２の空調用利用側分割熱交換器２８ｂを順に流れていく間に、空調用冷温水循環回路８内を流れる水から吸熱して蒸発し、自然に空調用冷媒バイパス配管２９を通って、中間熱交換器２３へと戻っていく。なお、この第２の自然循環経路が形成される際には、二方弁３５ｃ、二方弁３５ｄ、二方弁３５ｆ、および空調用補助膨張弁２７ｂは閉じており、空調用膨張弁２７は、適度な弁開度に調整されている。 Next, 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. In this second natural circulation path, 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. 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. When the second natural circulation path is formed, 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.

　次に、第３の自然循環経路は、分岐点Ｂ→分岐点Ｉ→分岐点Ｃ→分岐点Ｊ→分岐点Ｆ→分岐点Ｅ→分岐点Ａ→分岐点Ｂを辿る経路である。この第３の自然循環経路では、空調用熱源側熱交換器２４で大気と熱交換して液化した空調用冷媒は、密度差により自然に空調用冷媒タンク２６へと流れていき、空調用膨張弁２７を経由して第１の空調用利用側熱交換器２８ａ、第２の空調用利用側分割熱交換器２８ｂの順に流れていく。そして、液化した空調用冷媒は、第１の空調用利用側熱交換器２８ａおよび第２の空調用利用側分割熱交換器２８ｂで空調用冷温水循環回路８内を流れる水から吸熱して蒸発し、自然に空調用冷媒バイパス配管２９を通って、空調用熱源側熱交換器２４へと戻っていく。なお、この第３の自然循環経路が形成される際には、二方弁３５ａ、二方弁３５ｂ、二方弁３５ｆ、および空調用補助膨張弁２７ｂは閉じており、空調用膨張弁２７は、適度な弁開度に調整されている。 Next, 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. In this third natural circulation path, 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. Then, 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. When the third natural circulation path is formed, the two-way valve 35a, the two-way valve 35b, 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.

　次に、第４の自然循環経路は、分岐点Ｃ→分岐点Ｊ→分岐点Ｆ→分岐点Ｃを辿る経路である。この第４の自然循環経路では、空調用熱源側熱交換器２４で大気と熱交換して液化した空調用冷媒は、密度差により自然に空調用冷媒タンク２６へと流れていき、空調用膨張弁２７を経由して第１の空調用利用側熱交換器２８ａに流れていく。そして、液化した空調用冷媒は、第１の空調用利用側熱交換器２８ａで空調用冷温水循環回路８内を流れる水から吸熱して蒸発し、自然に第３の空調用冷媒バイパス配管２９ｃを通って、空調用熱源側熱交換器２４へと戻っていく。なお、この第３の自然循環経路が形成される際には、二方弁３５ａ、二方弁３５ｂ、二方弁３５ｃ、二方弁３５ｅ、および空調用補助膨張弁２７ｂは閉じており、空調用膨張弁２７は、適度な弁開度に調整されている。 Next, 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. In this fourth natural circulation path, 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. Then, 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. When 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.

　このように、第３の実施の形態例によれば、第１の自然循環経路～第４の自然循環経路の４パターンの自然循環式サイクルを形成することができるので、住宅６０の室内温度と室外温度との関係や室内の露点温度、その他の環境条件を考慮したうえで最適な自然循環式サイクルを制御装置１ａが選択することができる。よって、自然循環サイクルの活用のバリエーションが増え、空調用圧縮機２１を停止した運転を行える場合が増えるため、第３の実施の形態例に掛かる空調給湯システムは、空調サイクルの運転に掛かる消費電力を軽減することができる。 As described above, according to the third embodiment, since it is possible to form four patterns of natural circulation cycles of the first natural circulation path to the fourth natural circulation path, 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.

　なお、第３の実施の形態例に係る空調給湯システムでは、制御装置１ａが行う運転モードの選択の処理において、上記した（ｂ）給湯機運転可否の条件に、利用者の要求の有無だけでなく、タンク温度が予め定めた温度Ｔ１より大または小のどちらであるかを追加することができる（図９参照）。 In the air conditioning and hot water supply system according to the third embodiment, in the process of selecting the operation mode performed by the control device 1a, only the presence or absence of the user's request under the condition (b) whether the water heater can be operated or not. Instead, it can be added whether the tank temperature is higher or lower than the predetermined temperature T1 (see FIG. 9).

　１…ヒートポンプユニット、１ａ…制御装置、２…室内ユニット、５…空調用冷媒回路、６…給湯用冷媒回路、７…蓄熱・貯湯ユニット、８…空調用冷温水循環回路（空調用熱搬送媒体循環回路）、９…給湯回路、２１…空調用圧縮機、２２…四方弁（空調用流路切替弁）、２３…中間熱交換器、２４…空調用熱源側熱交換器、２７…空調用膨張弁、２８…空調用利用側熱交換器、２９…空調用冷媒バイパス配管（バイパス配管）、３４ａ、３４ｂ…三方弁（バイパス開閉手段）、４１…給湯用圧縮機、４２…給湯用利用側熱交換器、４３…給湯用膨張弁、４４…給湯用熱源側熱交換器、４６…給湯用冷媒タンク、６０…住宅（被空調空間）、６１…室内熱交換器、７０…貯湯タンク（タンク）、７１…蓄熱タンク（タンク）、ＴＥ１～ＴＥ８…温度センサ Reference Signs List 1 heat pump unit 1a control device 2 indoor unit 5 air conditioning refrigerant circuit 6 hot water supply refrigerant circuit 7 heat storage and hot water storage unit 8 air conditioning cold and hot water circulation circuit (heat transfer medium circulation for air conditioning Circuits, 9: Hot water supply circuit, 21: Air conditioning compressor, 22: Four-way valve (air conditioning flow path switching valve), 23: Intermediate heat exchanger, 24: Air conditioning heat source side heat exchanger, 27: Air conditioning expansion Valves 28: air conditioning use side heat exchangers, 29: air conditioning refrigerant bypass piping (bypass piping) 34a, 34b: three-way valve (bypass opening and closing means) 41: hot water supply compressor, 42: hot water use side heat Exchanger, 43: expansion valve for hot water supply, 44: heat source side heat exchanger for hot water supply, 46: refrigerant tank for hot water supply, 60: housing (air conditioned space), 61: indoor heat exchanger, 70: hot water storage tank (tank) 71: Heat storage tank (tank), TE1 to T 8 ... temperature sensor

Claims (5)

　冷房運転と暖房運転とを切替えて行う空調用冷媒回路と、給湯を行う給湯用冷媒回路と、前記空調用冷媒回路を循環する空調用冷媒と前記給湯用冷媒回路を循環する給湯用冷媒との間で熱交換を行う中間熱交換器とを備えた空調給湯システムであって、
　前記空調用冷媒回路を、空調用圧縮機、空調用流路切替弁、前記中間熱交換器、空調用膨張弁、空調用利用側の熱搬送媒体と熱交換を行うための空調用利用側熱交換器を順次冷媒配管で接続して環状に形成し、
　前記給湯用冷媒回路を、給湯用圧縮機、給湯用利用側の熱搬送媒体と熱交換を行う給湯用利用側熱交換器、給湯用膨張弁、前記中間熱交換器を順次冷媒配管で接続して環状に形成し、
　前記空調用冷媒回路に、前記空調用圧縮機をバイパスするバイパス配管と、前記空調用冷媒の流路を、前記空調用圧縮機を経由する流路と前記バイパス配管を経由する流路との何れかに切り替えるバイパス開閉手段とを設け、
　前記中間熱交換器を前記空調用利用側熱交換器より高い位置に設置した
　ことを特徴とする空調給湯システム。 A refrigerant circuit for air conditioning performed by switching between a cooling operation and a heating operation, a refrigerant circuit for hot water supply that performs hot water supply, an air conditioning refrigerant that circulates the refrigerant circuit for air conditioning, and a hot water supply refrigerant that circulates the refrigerant circuit for hot water supply An air-conditioning and hot-water supply system comprising: an intermediate heat exchanger for exchanging heat between each other;
The air conditioning use side heat exchanger for heat exchange with the air conditioning compressor, air conditioning flow path switching valve, the intermediate heat exchanger, the air conditioning expansion valve, and the heat transport medium on the air conditioning use side. The exchangers are sequentially connected by refrigerant piping to form an annular shape,
The hot water supply refrigerant circuit is connected to the hot water supply compressor, the hot water use side heat exchanger for exchanging heat with the hot water use side heat transfer medium, the hot water expansion valve, and the intermediate heat exchanger sequentially by means of a refrigerant pipe Form annularly,
The air conditioning refrigerant circuit includes any of a bypass pipe bypassing the air conditioning compressor, a flow path of the air conditioning refrigerant, a flow path passing through the air conditioning compressor, and a flow path passing through the bypass piping Provide a bypass switching means for switching to
An air conditioning and hot water supply system characterized in that the intermediate heat exchanger is installed at a position higher than the use side heat exchanger for air conditioning. 　請求項１の記載において、
　前記空調用冷媒回路に、空調用熱源側の熱搬送媒体と前記空調用冷媒との間で熱交換するための空調用熱源側熱交換器を前記中間熱交換器と並列にして設け、
　前記給湯用冷媒回路に、給湯用熱源側の熱搬送媒体と前記給湯用冷媒との間で熱交換するための給湯用熱源側熱交換器を前記中間熱交換器と並列にして設け、
　前記空調用熱源側熱交換器を前記空調用利用側熱交換器よりも高い位置に設置した
　ことを特徴とする空調給湯システム。 In the description of claim 1,
In the air conditioning refrigerant circuit, an air conditioning heat source side heat exchanger for exchanging heat between the air conditioning heat source side heat transfer medium and the air conditioning refrigerant is provided in parallel with the intermediate heat exchanger,
The hot water supply refrigerant circuit is provided with a hot water supply heat source side heat exchanger for exchanging heat between the hot water supply heat source side heat transfer medium and the hot water supply refrigerant in parallel with the intermediate heat exchanger;
An air conditioning and hot water supply system characterized in that the air conditioning heat source side heat exchanger is installed at a position higher than the air conditioning use side heat exchanger. 　請求項１または２の記載において、
　前記空調用利用側熱交換器と被空調空間に設置された室内熱交換器との間を配管で接続して空調用熱搬送媒体循環回路を形成し、前記空調用熱搬送媒体循環回路に前記空調用利用側の熱搬送媒体としての水またはブラインを循環させるようにしたことを特徴とする空調給湯システム。 In the description of claim 1 or 2,
The air-conditioning heat-transfer medium circulation circuit is formed by connecting the air-conditioning use side heat exchanger and the indoor heat exchanger installed in the air-conditioned space by piping to form the air-conditioning heat transfer medium circulation circuit. An air-conditioning and hot-water supply system characterized by circulating water or brine as a heat transfer medium on a use side for air-conditioning. 　請求項１～３のいずれか１項の記載において、
　前記給湯用利用側熱交換器の入口と出口に、前記給湯用利用側の熱搬送媒体としての水が流れる配管をそれぞれ接続して給湯回路を形成し、前記給湯回路に、水が前記給湯用利用側熱交換器から得た熱を蓄えることが可能なタンクを設けたことを特徴とする空調給湯システム。 In the description of any one of claims 1 to 3,
Piping through which water as the heat transfer medium on the use side for hot water supply flows is connected to the inlet and outlet of the use side heat exchanger for hot water supply respectively to form a hot water supply circuit, and the hot water supply circuit contains water for the hot water supply An air conditioning and hot water supply system characterized in that a tank capable of storing heat obtained from a use side heat exchanger is provided. 　請求項１～４のいずれか１項の記載において、
　前記空調用冷媒回路および前記給湯用冷媒回路の運転を制御する制御装置を備え、
　前記制御装置は、
　利用者によって設定される設定室温と、
　利用者によって設定される設定湿度と、
　外気温度と、
　前記空調用利用側の熱搬送媒体の前記空調用利用側熱交換器入口の温度と、
　前記設定室温、前記設定湿度および前記空調用利用側の熱搬送媒体の前記空調用利用側熱交換器入口の温度に基づいて決定される前記空調用利用側の熱搬送媒体の前記空調用利用側熱交換器出口の設定温度と、
　前記給湯用利用側の熱搬送媒体の前記給湯用利用側熱交換器入口の温度と、
　利用者の要求および前記給湯用利用側の熱搬送媒体の前記給湯用利用側熱交換器入口の温度に基づいて決定される給湯出力と、
　前記給湯用利用側の熱搬送媒体の前記給湯用利用側熱交換器出口の出湯温度と
　に基づいて、複数の運転モードの中から何れかを選択する
　ことを特徴とする空調給湯システム。 In the description of any one of claims 1 to 4,
A controller for controlling the operation of the air conditioning refrigerant circuit and the hot water supply refrigerant circuit;
The controller is
Set room temperature set by the user, and
Set humidity set by the user,
With the ambient temperature,
A temperature at the inlet side of the use-side heat exchanger for the air-conditioning use of the heat transfer medium on the use-side at the air-conditioning use;
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 Setting temperature of the heat exchanger outlet,
Temperature of the hot water use side heat exchanger inlet of the hot water use side heat transfer medium;
A hot water supply output determined based on the user's request and the temperature of the hot water use side heat exchanger inlet of the hot water use side heat transfer medium;
An air-conditioning and hot-water supply system, wherein any one of a plurality of operation modes is selected based on the hot-water temperature at the outlet of the use-side heat exchanger of the heat transfer medium on the use-side of the hot-water supply.
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