US20200200448A1 - Heat pump system - Google Patents

Heat pump system Download PDF

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Publication number
US20200200448A1
US20200200448A1 US16/640,084 US201716640084A US2020200448A1 US 20200200448 A1 US20200200448 A1 US 20200200448A1 US 201716640084 A US201716640084 A US 201716640084A US 2020200448 A1 US2020200448 A1 US 2020200448A1
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Prior art keywords
heat exchanger
air
refrigerant
auxiliary heat
conditioning apparatus
Prior art date
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Abandoned
Application number
US16/640,084
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English (en)
Inventor
Kazuhiro Ito
Shigeo Takata
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TAKATA, SHIGEO, ITO, KAZUHIRO
Publication of US20200200448A1 publication Critical patent/US20200200448A1/en
Abandoned legal-status Critical Current

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    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/26—Refrigerant piping
    • F24F1/32—Refrigerant piping for connecting the separate outdoor units to indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/006—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an air-to-air heat exchanger
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0252—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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]
    • Y02B30/56—Heat recovery units
    • 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]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present disclosure relates to a heat pump system that effectively uses exhaust heat.
  • Patent Literature 1 air-source heat pump type air-conditioning apparatuses have been proposed, which incorporate a total heat exchanger and a heat exchanger serving as an outdoor unit (see, for example, Patent Literature 1).
  • the air-conditioning apparatus described in Patent Literature 1 is installed in a building to perform indoor temperature control and ventilation.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 7-310964
  • Such a plurality of air-conditioning apparatuses as described in Patent Literature 1 may be installed in the same building.
  • the air-conditioning apparatus installed for the office room basically performs a heating operation
  • the air-conditioning apparatus installed for the computer room performs a cooling operation.
  • exhaust heat from the heat exchanger serving as the outdoor unit of the air-conditioning apparatus installed for the computer room is useful for the office room.
  • such exhaust heat has been let out outdoors without being effectively used.
  • exhaust heat from a heat exchanger serving as an outdoor unit of one of the air-conditioning apparatuses that is installed for a first space may be used for a second space that is different from the first space.
  • exhaust heat from the heat exchanger serving as the outdoor unit has been let out outdoors without being effectively used.
  • the present disclosure is applied to solve the above problem, and relates to a heat pump system in which exhaust heat from an outdoor heat exchanger installed for a first space is effectively used in a second space different from the first space, whereby an internal air-conditioning load in the second space can be reduced and an energy efficiency can be improved to achieve energy savings.
  • a heat pump system includes: a first air-conditioning apparatus that includes a compressor, an outdoor-side heat exchanger, an expansion device, and an indoor-side heat exchanger, and that air-conditions a first space; a ventilator that includes a first auxiliary heat exchanger, and ventilates and air-conditions a second space different from the first space; and a refrigerant circuit in which the compressor, the outdoor-side heat exchanger, the first auxiliary heat exchanger, the expansion device, and the indoor-side heat exchanger are sequentially connected by a refrigerant pipe to allow refrigerant to circulate.
  • the first auxiliary heat exchanger is provided in a supply air passage in the ventilator.
  • the heat pump system includes the refrigerant circuit in which the compressor, the outdoor-side heat exchanger, the first auxiliary heat exchanger, the expansion device, and the indoor-side heat exchanger are sequentially connected by the refrigerant pipe to allow refrigerant to circulate, and the first auxiliary heat exchanger is provided in the supply air passage of the ventilator. Because of this configuration, exhaust heat from the outdoor-side heat exchanger installed for the first space can be used to regulate the temperature of air supplied from the ventilator installed for the second space different from the first space. It is therefore possible to reduce the internal air-conditioning load in the second space and improve an energy efficiency to achieve energy savings.
  • FIG. 1 is a schematic diagram illustrating a configuration of a heat pump system according to Embodiment 1 of the present disclosure.
  • FIG. 2 is a first detailed configuration diagram of the heat pump system according to Embodiment 1 of the present disclosure.
  • FIG. 3 is a second detailed configuration diagram of the heat pump system according to Embodiment 1 of the present disclosure.
  • FIG. 4 indicates an example of conditions for controlling a second flow switching device of the heat pump system according to Embodiment 1 of the present disclosure.
  • FIG. 5 illustrates a control flow diagram of the heat pump system according to Embodiment 1 of the present disclosure.
  • FIG. 6 is a detailed configuration diagram of a heat pump system according to Embodiment 2 of the present disclosure.
  • FIG. 7 indicates an example of conditions for controlling a second flow switching device of the heat pump system according to Embodiment 2 of the present disclosure.
  • FIG. 8 is a control flow diagram of the heat pump system according to Embodiment 2 of the present disclosure.
  • FIG. 9 is a detailed configuration diagram of a heat pump system according to Embodiment 3 of the present disclosure.
  • FIG. 10 indicates an example of conditions for controlling a second flow switching device of the heat pump system according to Embodiment 3 of the present disclosure.
  • FIG. 11 is a control flow diagram of the heat pump system according to Embodiment 3 of the present disclosure.
  • FIG. 12 is a diagram illustrating an example of the second flow switching device of the heat pump system according to Embodiment 3 of the present disclosure.
  • FIG. 13 is a diagram illustrating another example of the second flow switching device of the heat pump system according to Embodiment 3 of the present disclosure.
  • FIG. 14 illustrates examples of an operation of the second flow switching device of the heat pump system according to Embodiment 3 of the present disclosure operates.
  • FIG. 15 is a first detailed configuration diagram of a heat pump system according to Embodiment 4 of the present disclosure.
  • FIG. 16 is a second detailed configuration diagram of the heat pump system according to Embodiment 4 of the present disclosure.
  • FIG. 1 is a schematic diagram illustrating a configuration of a heat pump system 100 according to Embodiment 1 of the present disclosure.
  • the heat pump system 100 includes an air-conditioning apparatus 40 , a ventilator 53 , and a controller 54 .
  • the air-conditioning apparatus 40 is installed for a first space 101 , and air-conditions the first space 101 .
  • the air-conditioning apparatus 40 includes an indoor unit 51 and an outdoor unit 52 .
  • the ventilator 53 is installed for a second space 102 , and ventilates and air-conditions the second space 102 .
  • the indoor unit 51 , the outdoor unit 52 , and the ventilator 53 are connected by a refrigerant pipe 1 .
  • the first space 101 and the second space 102 are different spaces.
  • the controller 54 is housed in the indoor unit 52 .
  • the controller 54 is connected to the indoor unit 51 , the outdoor unit 52 , and the ventilator 53 by communication transmission lines 2 .
  • the controller 54 monitors the operating state of each of devices (the indoor unit 51 , the outdoor unit 52 , and the ventilator 53 ), and gives an output instruction to each of actuators of he devices.
  • a remote control unit 56 is connected to the controller 54 either wirelessly or by a signal line. It is therefore possible to change, using the remote control unit 56 , an on/off state such as whether each device is in operation or stopped state, i.e., in on state or off state, an operation mode, a set temperature, the amount of air, etc., of each device.
  • controller 54 is provided in the outdoor unit 52 , it is not limited where the controller 54 is provided.
  • the controller 54 may be provided in the indoor unit 51 .
  • An air-conditioning apparatus 41 as illustrated in FIG. 1 will be described later on.
  • FIG. 2 is a first detailed configuration diagram of the heat pump system 100 according to Embodiment 1 of the present disclosure.
  • FIG. 3 is a second detailed configuration diagram of the heat pump system 100 according to Embodiment 1 of the present disclosure.
  • the indoor unit 51 includes an indoor-side heat exchanger 7 , an expansion device 8 , and an indoor fan 21 .
  • the outdoor unit 52 includes a compressor 3 , a first flow switching device 4 , an outdoor-side heat exchanger 5 , an outdoor fan 6 , and a second flow switching device 9 .
  • the ventilator 53 includes a total heat exchanger 10 , a supply air fan 13 , an exhaust air fan 14 , a first auxiliary heat exchanger 15 , and an outside-air temperature sensor 17 .
  • the heat pump system 100 includes a refrigerant circuit in which the compressor 3 , the first flow switching device 4 , the outdoor-side heat exchanger 5 , the second flow switching device 9 , the first auxiliary heat exchanger 15 , the expansion device 8 , and the indoor-side heat exchanger 7 are sequentially connected by refrigerant pipes 1 to allow refrigerant to circulate.
  • the refrigerant circuit includes a bypass 18 that bypasses the first auxiliary heat exchanger 15 .
  • the first flow switching device 4 switches the flow direction of refrigerant between an ⁇ -direction (indicated by a solid line in FIG. 3 ) in which the refrigerant flows from the discharge side of the compressor 3 toward the outdoor-side heat exchanger 5 and a ⁇ -direction (indicated by a broken line in FIG. 3 ) in which the refrigerant flows from the discharge side of the compressor 3 toward the indoor-side heat exchanger 7 .
  • the first flow switching device 4 is, for example, a four-way valve.
  • the second flow switching device 9 switches the flow direction of refrigerant between a first direction (corresponding to passage ( 1 ) in FIG. 3 ) in which the refrigerant bypasses the first auxiliary heat exchanger 15 and passes through the bypass 18 and a second direction (corresponding to passage ( 2 ) in FIG. 3 ) in which the refrigerant passes through the first auxiliary heat exchanger 15 .
  • the second flow switching device 9 is, for example, a three-way valve.
  • the first flow switching device 4 switches the flow direction of the refrigerant to the ⁇ -direction.
  • the second flow switching device 9 switches the flow direction of the refrigerant to the first direction
  • high-temperature, high-pressure refrigerant discharged by the compressor 3 passes through the outdoor-side heat exchanger 5 and condenses.
  • the second flow switching device 9 switches the flow direction of the refrigerant to the second direction
  • the high-temperature, high-pressure refrigerant discharged by the compressor 3 sequentially passes through the outdoor-side heat exchanger 5 and the first auxiliary heat exchanger 15 and condenses.
  • the refrigerant that has condensed is reduced in pressure by the expansion device 8 to change into low-temperature, low-pressure refrigerant.
  • the low-temperature, low-pressure refrigerant flows into the indoor-side heat exchanger 7 , exchanges heat with indoor air in the first space 101 , and evaporates.
  • the refrigerant that has evaporated is sucked into the compressor 3 and compressed thereby into high-temperature, high-pressure refrigerant.
  • the high-temperature, high-pressure refrigerant is re-discharged from the compressor 3 .
  • the refrigerant is repeatedly subjected to the above processes and flows in the above manner.
  • air subjected to heat exchange at the indoor-side heat exchanger 7 is blown out into the first space 101 .
  • the first flow switching device 4 switches the flow direction of refrigerant to the ⁇ -direction.
  • the high-temperature, high-pressure refrigerant discharged by the compressor 3 flows into the indoor-side heat exchanger 7 , exchanges heat with indoor air in the first space 101 , and condenses.
  • the refrigerant that has condensed is reduced in pressure by the expansion device 8 .
  • the second flow switching device 9 switches the flow direction of the refrigerant to the first direction, the refrigerant that has been reduced in pressure passes through the outdoor-side heat exchanger 5 and evaporates.
  • the second flow switching device 9 switches the flow direction of the refrigerant to the second direction, the refrigerant that has been reduced in pressure sequentially passes through the first auxiliary heat exchanger 15 and the outdoor-side heat exchanger 5 and evaporates.
  • the refrigerant that has evaporated is sucked into the compressor 3 , and compressed into high-temperature, high-pressure refrigerant.
  • the high-temperature, high-pressure refrigerant is re-discharged from the compressor 3 .
  • the refrigerant is repeatedly subjected to the above processes and flows in the above manner.
  • air subjected to heat exchange at the indoor-side heat exchanger 7 is blown out into the first space 101 .
  • the ventilator 53 causes air taken in from the outdoor space to exchange heat with air let out from the second space 102 , and then supplies the air into the second space 102 .
  • the supply air fan 13 produces, in a supply air passage 11 , an air flow for taking air from the outdoor space into the second space 102 .
  • the exhaust air fan 14 produces, in an exhaust air passage 12 , an air flow for letting out air from the second space 102 to the outdoor space.
  • the total heat exchanger 10 causes heat exchange to be performed between air that flows in the supply air passage 11 and air that flows in the exhaust air passage 12 .
  • the first auxiliary heat exchanger 15 is installed in part of the supply air passage 11 that is located leeward of the total heat exchanger 10 , i.e., that is located between the total heat exchanger 10 and the supply air fan 13 .
  • the first auxiliary heat exchanger 15 causes air that has passed through the total heat exchanger 10 to exchange heat with refrigerant.
  • the ventilator 53 is also configured to cause air taken from the outdoor space into the ventilator 53 to pass through the total heat exchanger 10 and then pass through the first auxiliary heat exchanger 15 . Because of this configuration, heat is not taken away by exhaust air, and can thus be efficiently used. After passing through the first auxiliary heat exchanger 15 , the air is supplied into the second space 102 .
  • outside-air temperature sensor 17 is provided in part of the supply air passage 11 that is located windward of the total heat exchanger 10 .
  • the outside-air temperature sensor 17 is, for example, a thermistor, and detects the temperature of outside air, i.e., outside air temperature.
  • Information on the outside air temperature detected by the outside-air temperature sensor 17 (which will be hereinafter referred to as outside-air temperature information) is sent to the controller 54 .
  • the outside-air temperature sensor 17 is included in the ventilator 53 , this is not limitative. Also, it is not limited where the outside-air temperature sensor 17 is provided. For example, the outside-air temperature sensor 17 may be installed outside the ventilator 53 .
  • the amount of heat that is transferred at the outdoor-side heat exchanger 5 and that at the first auxiliary heat exchanger 15 can be regulated. Because of this regulation, the amount of condensation at the outdoor-side heat exchanger 5 and that at the first auxiliary heat exchanger 15 are controlled, whereby the operation of the refrigeration cycle circuit is stabilized, and the amount of heat that is transferred at the first auxiliary heat exchanger 15 is regulated. Thus, the amount of heat that is supplied to the second space 102 can be regulated.
  • the rotation speed of the outdoor fan 6 is set lower than in the case where the refrigerant is not made to flow through the first auxiliary heat exchanger 15 .
  • the refrigerant is made to flow through the first auxiliary heat exchanger 15 , it is appropriate that the rotation speed of the outdoor fan 6 , the rotation speed of the supply air fan 13 , and the rotation speed of the exhaust air fan 14 are regulated.
  • the amount of heat that is transferred at the outdoor-side heat exchanger 5 and that at the first auxiliary heat exchanger 15 can be regulated. Because of this regulation, the amount of evaporation at the outdoor-side heat exchanger 5 and that at the first auxiliary heat exchanger 15 are controlled, whereby the operation of the refrigeration cycle circuit is stabilized, and the amount of heat that is transferred at the first auxiliary heat exchanger 15 is regulated. Thus, the amount of heat that is supplied to the second space 102 can be regulated.
  • the rotation speed of the outdoor fan 6 is set lower than in the case where the refrigerant is not passed through the first auxiliary heat exchanger 15 .
  • heat that is released to the outdoor space by the outdoor-side heat exchanger 5 can be used to air-condition the second space 102 . That is, since the heat pump system 100 according to Embodiment 1 can perform air-conditioning using exhaust heat, the energy efficiency of the entire heat pump system 100 can be improved to achieve energy savings. Also, in the heat pump system 100 according to Embodiment 1, the amount of heat that is transferred at the outdoor-side heat exchanger 5 can be reduced, heat-island phenomenon and cold-island phenomenon can thus be reduced.
  • FIG. 4 indicates an example of the conditions for controlling the second flow switching device 9 of the heat pump system 100 according to Embodiment 1 of the present disclosure.
  • “ ⁇ ” means that related determinations are made regardless of the conditions indicated by “ ⁇ ”.
  • the air-conditioning apparatus 41 (see FIG. 1 ) is installed in the second space 102 .
  • the air-conditioning apparatus 41 is different from the air-conditioning apparatus 40 installed in the first space 101 .
  • the air-conditioning apparatus 41 air-conditions the second space 102 using the refrigeration cycle circuit.
  • the air-conditioning apparatus 41 is connected to the controller 54 by a communication transmission line 2 .
  • the heat pump system 100 determines the flow direction of the refrigerant that is to be set by the second flow switching device 9 , based on the operating states (operation mode and thermo-state) of the air-conditioning apparatus 40 installed in the first space 101 , the operating states (operation mode and thermo-state) of the air-conditioning apparatus 41 installed in the second space 102 , and the operating state of the ventilator 53 installed in the second space 102 (whether the ventilator 53 is in operation or stopped state).
  • FIG. 5 is a control flow diagram of the heat pump system 100 according to Embodiment 1 of the present disclosure.
  • the controller 54 acquires the operation information on the air-conditioning apparatus 40 installed in the first space 101 (step S 101 ) and also acquires the operation information on the air-conditioning apparatus 41 and ventilator 53 installed in the second space 102 (step S 102 ). The controller 54 also acquires the outside-air temperature information (step S 103 ).
  • the operation information on the air-conditioning apparatus 40 includes the operation mode and the thermo-state of the air-conditioning apparatus 40 .
  • the operation information on the air-conditioning apparatus 41 includes the operation mode and the thermo-state of the air-conditioning apparatus 41 .
  • the operation information on the ventilator 53 includes on/off state information indicating whether the ventilator 53 is in operation or stopped state.
  • step S 103 the controller 54 determines, on the basis of each operation information, whether the operation mode of the air-conditioning apparatus 40 is the same as the operation mode of the air-conditioning apparatus 41 or not (step S 104 ).
  • step S 104 When determining in step S 104 that the operation mode of the air-conditioning apparatus 40 is the same as the operation mode of the air-conditioning apparatus 41 (YES in step S 104 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the first direction (step S 105 ).
  • step S 105 when the controller 54 determines that the operation mode of the air-conditioning apparatus 40 is different from the operation mode of the air-conditioning apparatus 41 (NO in step S 104 ), the process proceeds to step S 106 .
  • step S 106 the controller 54 determines, on the basis of each operation information, whether or not the air-conditioning apparatus 40 is in thermo-on state and the air-conditioning apparatus 41 is in thermo-on state.
  • air-conditioning apparatus 40 is in thermo-on state
  • air-conditioning apparatus 41 is thermo-on state
  • a compressor (not illustrated) of the air-conditioning apparatus 41 is in operation.
  • step S 106 When determining in step S 106 that at least one of the air-conditioning apparatus 40 and the air-conditioning apparatus 41 is not in thermo-on state (NO in step S 106 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the first direction (step S 110 ).
  • step S 110 the controller 54 determines that the air-conditioning apparatus 40 is in thermo-on state and the air-conditioning apparatus 41 is also in thermo-on state (YES in step S 106 )
  • the process proceeds to step S 107 .
  • step S 107 the controller 54 determines, on the basis of each operation information, whether the ventilator 53 is in operation or not.
  • the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the first direction (step S 110 ).
  • the process proceeds to step S 108 .
  • step S 108 the controller 54 determines, on the basis of outside-air temperature information, whether the outside air temperature is higher than a first temperature set in advance and is lower than a second temperature set in advance.
  • the first temperature is a low temperature threshold at which the operation of the refrigeration cycle circuit becomes unstable
  • the second temperature is a high temperature threshold at which the operation of the refrigeration cycle circuit becomes unstable.
  • step S 108 When determining in step S 108 that the outside air temperature is higher than the first temperature and lower than the second temperature (YES in step S 108 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the second direction (step S 109 ).
  • step S 110 when determining that the outside air temperature is lower than or equal to the first temperature, or higher than or equal to the second temperature (NO in step S 108 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the first direction (step S 110 ).
  • the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the second direction in accordance with the outside air temperature.
  • exhaust heat from the air-conditioning apparatus 40 installed in the first space 101 can be used in the second space 102 . It is therefore possible to reduce the internal air-conditioning load in the second space 102 and improve the energy efficiency of the heat pump system 100 to achieve energy savings.
  • the flow direction set by the second flow switching device 9 is not switched to the second direction.
  • priority is given to control of the ventilation. It is therefore hard to control the amount of air in the supply air passage 11 or the exhaust air passage 12 of the ventilator 53 in such a manner as to stabilize the operation of the refrigeration cycle circuit.
  • the flow direction set by the second flow switching device 9 is switched to the first direction to give priority to stabilization of the operation of the refrigeration cycle circuit.
  • the heat pump system 100 according to Embodiment 1 can be simply configured to incorporate an auxiliary heat exchanger unit 500 (see FIG. 3 ) in which the second flow switching device 9 and the first auxiliary heat exchanger 15 are connected by the refrigerant pipe 1 . That is, the heat pump system 100 can be formed simply by connecting the auxiliary heat exchanger unit 500 to an existing refrigeration cycle apparatus.
  • the heat pump system 100 of Embodiment 1 is not limited to the example described above. To be more specific, it is not indispensable that the first auxiliary heat exchanger 15 is provided in the supply air passage 11 . That is, it suffices that the first auxiliary heat exchanger 15 is provided in the second space 102 different from the first space 101 to supply heat to the second space 102 .
  • the heat pump system 100 includes: the air-conditioning apparatus 40 that includes the compressor 3 , the outdoor-side heat exchanger 5 , the expansion device 8 , and the indoor-side heat exchanger 7 , and that air-conditions the first space 101 ; the ventilator 53 that includes the first auxiliary heat exchanger 15 , and ventilates and air-conditions the second space 102 different from the first space 101 ; and the refrigerant circuit in which the compressor 3 , the outdoor-side heat exchanger 5 , the first auxiliary heat exchanger 15 , the expansion device 8 , and the indoor-side heat exchanger 7 are sequentially connected by the refrigerant pipes 1 to allow refrigerant to circulate.
  • the first auxiliary heat exchanger 15 is provided in the supply air passage 11 of the ventilator 53 .
  • the heat pump system 100 includes the refrigerant circuit in which the compressor 3 , the outdoor-side heat exchanger 5 , the first auxiliary heat exchanger 15 , the expansion device 8 , and the indoor-side heat exchanger 7 are sequentially connected by the refrigerant pipes 1 to allow refrigerant to circulate.
  • the first auxiliary heat exchanger 15 is provided in the supply air passage 11 of the ventilator 53 . Because of this configuration, exhaust heat from the outdoor-side heat exchanger 5 installed for the first space 101 can be used to regulate the temperature of air that is supplied from the ventilator 53 installed for the second space 102 different from the first space 101 . It is therefore possible to reduce the internal air-conditioning load in the second space 102 and improve the energy efficiency to achieve energy savings.
  • the first auxiliary heat exchanger 15 is provided in the part of the supply air passage 11 that is located leeward of the total heat exchanger 10 .
  • the heat pump system 100 according to Embodiment 1 is configured to cause air taken from the outdoor space into the ventilator 53 to pass through the total heat exchanger 10 and then pass through the first auxiliary heat exchanger 15 . It is therefore possible to prevent heat from being removed by exhaust air and thus efficiently use heat.
  • the controller 54 causes the second flow switching device 9 to switch the flow passage for the refrigerant to the flow passage in which the refrigerant flows into the first auxiliary heat exchanger 15 , when the following first condition is satisfied: the operation mode of the air-conditioning apparatus 40 that air-conditions the first space 101 is different from that of the air-conditioning apparatus 41 that air-conditions the second space 102 ; the compressor 3 of the air-conditioning apparatus 40 and the compressor (not illustrated) of the air-conditioning apparatus 41 are both in operation; and the ventilator 53 is in operation.
  • the second flow switching device 9 is controlled in the above manner, whereby exhaust heat from the air-conditioning apparatus 40 installed in the first space 101 can be used in the second space 102 . It is therefore possible to reduce the internal air-conditioning load in the second space 102 and improve the energy efficiency of the heat pump system 100 to achieve energy savings.
  • the controller 54 when the first condition is satisfied and the outside air temperature is lower than or equal to the predetermined first temperature or higher than or equal to the second temperature set in advance and higher than the first temperature, the controller 54 causes the second flow switching device 9 to switch the flow passage for the refrigerant to a flow passage in which the refrigerant flows into the bypass 18 .
  • the heat pump system 100 according to Embodiment 1 can give priority to stabilization of the operation of the refrigeration cycle circuit.
  • Embodiment 2 of the present disclosure will be described. It should be noted that with respect to Embodiment 2, part of the above description regarding Embodiment 1 that can also be applied to Embodiment 2 will not be repeated, and components that are the same as or equivalent to those in Embodiment 1 will be denoted by the same reference signs.
  • FIG. 6 is a detailed configuration diagram of the heat pump system 100 according to Embodiment 2 of the present disclosure.
  • the first auxiliary heat exchanger 15 is provided in the part of the supply air passage 11 that is located between the total heat exchanger 10 and the supply air fan 13
  • a second auxiliary heat exchanger 16 is provided in part of the exhaust air passage 12 that is located between the total heat exchanger 10 and the exhaust air fan 14 .
  • the heat pump system 100 includes a refrigerant circuit in which the compressor 3 , the first flow switching device 4 , the outdoor-side heat exchanger 5 , the second flow switching device 9 , the first auxiliary heat exchanger 15 , the expansion device 8 , and the indoor-side heat exchanger 7 are sequentially connected by the refrigerant pipes 1 to allow refrigerant to circulate. Furthermore, in the refrigerant circuit, the second auxiliary heat exchanger 16 is connected in parallel with the first auxiliary heat exchanger 15 .
  • the second flow switching device 9 switches the flow direction of the refrigerant to one of the second direction (corresponding to passage ( 2 ) in FIG. 6 ) in which the refrigerant flows through the first auxiliary heat exchanger 15 and a third direction (corresponding to passage ( 3 ) in FIG. 6 ) in which the refrigerant flows through the second auxiliary heat exchanger 16 .
  • the second auxiliary heat exchanger 16 causes air that has passed through the total heat exchanger 10 to exchange heat with the refrigerant.
  • the ventilator 53 is configured to cause air taken from the indoor space into the ventilator 53 to pass through the total heat exchanger 10 and then pass through the second auxiliary heat exchanger 16 . Because of this configuration, heat can be efficiently used. After passing through the second auxiliary heat exchanger 16 , the air is let out to the outdoor space.
  • the second auxiliary heat exchanger 16 operates together with the outdoor-side heat exchanger 5 to let out heat for air-conditioning. Since the second auxiliary heat exchanger 16 functions, the amount of heat exchange at the outdoor-side heat exchanger 5 can be reduced.
  • the outdoor-side heat exchanger 5 and the second auxiliary heat exchanger 16 both operate as condensers.
  • the first space 101 is cooled and cool air from the first space 101 flows through the exhaust air passage 12 .
  • the second auxiliary heat exchanger 16 can condense the refrigerant using the cool air that flows through the exhaust air passage 12 . That is, the second auxiliary heat exchanger 16 can efficiently condense the refrigerant. It is therefore possible to reduce the amount of heat exchange at the outdoor-side heat exchanger 5 .
  • the outdoor-side heat exchanger 5 and the second auxiliary heat exchanger 16 both operate as evaporators.
  • the first space 101 is warmed up, and warm air from the first space 101 flows through the exhaust air passage 12 .
  • the second auxiliary heat exchanger 16 evaporates the refrigerant using the warm air that flows through the exhaust air passage 12 . That is, the second auxiliary heat exchanger 16 can efficiently evaporate the refrigerant. It is therefore possible to reduce the amount of heat exchange at the outdoor-side heat exchanger 5 .
  • the ventilator 53 is configured to cause air taken from the room into the ventilator 53 to pass through the total heat exchanger 10 and then pass through the second auxiliary heat exchanger 16 . Because of this configuration, priority is given to heat exchange of air that flows in the indoor space. Therefore, comfortability of the indoor space is ensured, and the energy efficiency of the air-conditioning apparatus 40 is improved to achieve energy savings.
  • FIG. 7 indicates an example of conditions for controlling the second flow switching device 9 of the heat pump system 100 according to Embodiment 2 of the present disclosure.
  • “ ⁇ ” means that related determinations are made regardless of the conditions indicated by “ ⁇ ”.
  • the air-conditioning apparatus 41 (see FIG. 1 ) is installed in the second space 102 .
  • the air-conditioning apparatus 41 is different from the air-conditioning apparatus 40 installed in the first space 101 .
  • the air-conditioning apparatus 41 air-conditions the second space 102 using a refrigeration cycle circuit.
  • the air-conditioning apparatus 41 is connected to the controller 54 by the communication transmission line 2 .
  • the heat pump system 100 determines the direction to which the flow direction set by the second flow switching device 9 is to be switched, based on the following condition: the operating state (operation mode and thermo-state) of the air-conditioning apparatus 40 installed in the first space 101 ; the operating state (operation mode and thermo-state) of the air-conditioning apparatus 41 installed in the second space 102 ; and the operating state of the ventilator 53 installed in the second space 102 (whether the ventilator 53 is in operation or stopped state).
  • FIG. 8 is a control flow diagram of the heat pump system 100 according to Embodiment 2 of the present disclosure.
  • the controller 54 acquires the operation information on the air-conditioning apparatus 40 installed in the first space 101 (step S 201 ) and also acquires the operation information on the air-conditioning apparatus 41 and ventilator 53 installed in the second space 102 (step S 202 ). The controller 54 also acquires the outside-air temperature information (step S 203 ).
  • the operation information on the air-conditioning apparatus 40 includes the operation mode and the thermo-state of the air-conditioning apparatus 40 .
  • the operation information on the air-conditioning apparatus 41 includes the operation mode and the thermo-state of the air-conditioning apparatus 41 .
  • the operation information on the ventilator 53 includes the on/off information of the ventilator 53 .
  • step S 203 the controller 54 determines, on the basis of each operation information, whether the operation mode of the air-conditioning apparatus 40 is the same as that of the air-conditioning apparatus 41 (step S 204 ).
  • step S 204 When determining in step S 204 that the operation mode of the air-conditioning apparatus 40 is the same as that of the air-conditioning apparatus 41 (YES in step S 204 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the third direction (step S 205 ).
  • the controller 54 determines that the operation mode of the air-conditioning apparatus 40 is different from the operation mode of the air-conditioning apparatus 41 (NO in step S 204 )
  • the process proceeds to step S 206 .
  • step S 206 the controller 54 determines, on the basis of each operation information, whether or not the air-conditioning apparatus 40 is in thermo-on state and the air-conditioning apparatus 41 is in thermo-on state.
  • air-conditioning apparatus 40 is in thermo-on state
  • air-conditioning apparatus 41 is in thermo-on state
  • the compressor (not illustrated) of the air-conditioning apparatus 41 is in operation.
  • step S 206 When determining in step S 206 that at least one of the air-conditioning apparatuses 40 and 41 is not in thermo-on state (NO in step S 206 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the third direction (step S 210 ). By contrast, when the controller 54 determines that the air-conditioning apparatuses 40 and 41 are both in thermo-on state (YES in step S 206 ), the process proceeds to step S 207 .
  • step S 207 the controller 54 determines, on the basis of each operation information, whether the ventilator 53 is in operation.
  • the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the third direction (step S 210 ).
  • the process proceeds to step S 208 .
  • step S 208 the controller 54 determines, on the basis of the outside-air temperature information, whether or not the outside air temperature is higher than a first temperature set in advance and lower than a second temperature set in advance.
  • the first temperature is a low temperature threshold at which the operation of the refrigeration cycle becomes unstable
  • the second temperature is a high temperature threshold at which the operation of the refrigeration cycle becomes unstable.
  • step S 208 When determining in step S 208 that the outside air temperature is higher than the first temperature and lower than the second temperature (YES in step S 208 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the second direction (step S 209 ).
  • the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the third direction (step S 210 ).
  • the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the second direction.
  • exhaust heat from the air-conditioning apparatus 40 installed in the first space 101 can be used in the second space 102 . It is therefore possible to reduce the internal air-conditioning load in the second space 102 and improve the energy efficiency of the entire heat pump system 100 to achieve energy savings.
  • the second auxiliary heat exchanger 16 can be made to perform part of heat exchange that should be performed at the outdoor-side heat exchanger 5 of the air-conditioning apparatus 40 .
  • the flow rate of air to be sent by the outdoor fan 6 in the air-conditioning apparatus 40 can be reduced.
  • the rotation speed of the outdoor fan 6 can be reduced, it is possible to achieve energy savings and reduce nose.
  • the flow direction set by the second flow switching device 9 is not switched to the second direction.
  • priority is given to control of the ventilation. It is therefore hard to control the amount of air in the supply air passage 11 or the exhaust air passage 12 of the ventilator 53 in such a manner as to stabilize the operation of the refrigeration cycle circuit.
  • the flow direction set by the second flow switching device 9 is switched to the third direction to give priority to stabilization of the operation of the refrigeration cycle circuit.
  • the second auxiliary heat exchanger 16 is provided in the part of the exhaust air passage 12 that is located leeward of the total heat exchanger 10 .
  • the heat pump system 100 according to Embodiment 2 is configured to cause air taken from the room into the ventilator 53 to pass through the total heat exchanger 10 and then pass through the second auxiliary heat exchanger 16 . It is therefore possible to efficiently use heat.
  • the controller 54 causes the second flow switching device 9 to switch the flow passage for the refrigerant to the flow passage in which the refrigerant flows into the first auxiliary heat exchanger 15 , when the following first condition is satisfied: the operation mode of the air-conditioning apparatus 40 that air-conditions the first space 101 is different from that of the air-conditioning apparatus 41 that air-conditions the second space 102 ; the compressor 3 of the air-conditioning apparatus 40 and the compressor (not illustrated) of the air-conditioning apparatus 41 are both in operation; and the ventilator 53 is in operation.
  • the second flow switching device 9 is controlled in the above manner, whereby exhaust heat from the air-conditioning apparatus 40 installed in the first space 101 can be used in the second space 102 . It is therefore possible to reduce the internal air-conditioning load in the second space 102 and improve the energy efficiency of the heat pump system 100 to achieve energy savings.
  • the controller 54 when the first condition is satisfied, and the outside air temperature is lower than or equal to the first temperature set in advance or higher than or equal to the second temperature set in advance and higher than the first temperature, the controller 54 causes the second flow switching device 9 to switch the flow passage for the refrigerant to the flow passage in which the refrigerant flows into the second auxiliary heat exchanger 16 .
  • the heat pump system 100 according to Embodiment 2 can give priority to stabilization of the operation of the refrigeration cycle.
  • Embodiment 3 of the present disclosure will be described. It should be noted that part of the above descriptions regarding Embodiments 1 and 2 that can also be applied to Embodiment 3 will not be repeated, and components that are the same as or equivalent to those in each of Embodiments 1 and 2 will be denoted by the same reference signs.
  • FIG. 9 is a detailed configuration diagram of the heat pump system 100 according to Embodiment 3 of the present disclosure.
  • the first auxiliary heat exchanger 15 is installed in part of the supply air passage 11 that is located between the total heat exchanger 10 and the supply air fan 13
  • the second auxiliary heat exchanger 16 is installed in part of the exhaust air passage 12 that is located between the total heat exchanger 10 and the exhaust air fan 14 .
  • the heat pump system 100 includes the refrigerant circuit in which the compressor 3 , the first flow switching device 4 , the outdoor-side heat exchanger 5 , the second flow switching device 9 , the first auxiliary heat exchanger 15 , the expansion device 8 , and the indoor-side heat exchanger 7 are sequentially connected by the refrigerant pipes 1 to allow refrigerant to circulate. Also, in the refrigerant circuit, the second auxiliary heat exchanger 16 is connected in parallel with the first auxiliary heat exchanger 15 .
  • the refrigerant circuit includes the bypass 18 that bypasses the first auxiliary heat exchanger 15 and the second auxiliary heat exchanger 16 .
  • the second flow switching device 9 switches the flow direction of refrigerant to one of the first direction (corresponding to passage ( 1 ) in FIG. 9 ) in which the refrigerant bypasses the first auxiliary heat exchanger 15 and the second auxiliary heat exchanger 16 and flows through the bypass 18 , the second direction (corresponding to passage ( 2 ) in FIG. 9 ) in which the refrigerant flows through the first auxiliary heat exchanger 15 , and the third direction (corresponding to passage ( 3 ) in FIG. 9 ) in which the refrigerant flows through the second auxiliary heat exchanger 16 .
  • FIG. 10 indicates an example of conditions for controlling the second flow switching device 9 of the heat pump system 100 according to Embodiment 3 of the present disclosure.
  • “ ⁇ ” means that related determinations are made regardless of the conditions indicated by “ ⁇ ”.
  • the air-conditioning apparatus 41 (see FIG. 1 ) is installed in the second space 102 .
  • the air-conditioning apparatus 41 is different from the air-conditioning apparatus 40 installed in the first space 101 .
  • the air-conditioning apparatus 41 air-conditions the second space 102 using the refrigeration cycle circuit.
  • the air-conditioning apparatus 41 is connected to the controller 54 by the communication transmission line 2 .
  • the heat pump system 100 determines the flow direction to be set by the second flow switching device 9 based on the following condition: the operating state (operation mode and thermo-state) of the air-conditioning apparatus 40 installed in the first space 101 ; the operating state (operation mode and thermo-state) of the air-conditioning apparatus 41 installed in the second space 102 ; and the operating state of the ventilator 53 installed in the second space 102 (whether the ventilator 53 is in operation or stopped state).
  • FIG. 11 is a control flow diagram of the heat pump system 100 according to Embodiment 3 of the present disclosure.
  • the controller 54 acquires the operation information on the air-conditioning apparatus 40 installed in the first space 101 (step S 301 ) and also acquires the operation information on the air-conditioning apparatus 41 and ventilator 53 installed in the second space 102 (step S 302 ). Furthermore, the controller 54 acquires the outside-air temperature information (step S 303 ).
  • the operation information on the air-conditioning apparatus 40 includes the operation mode and the thermo-state of the air-conditioning apparatus 40 .
  • the operation information on the air-conditioning apparatus 41 includes the operation mode and the thermo-state of the air-conditioning apparatus 41 .
  • the operation information on the ventilator 53 includes the on/off information of the ventilator 53 .
  • step S 303 the controller 54 determines, on the basis of each operation information, whether the operation mode of the air-conditioning apparatus 40 is the same as the operation mode of the air-conditioning apparatus 41 (step S 304 ).
  • step S 304 When determining in step S 304 that the operation mode of the air-conditioning apparatus 40 is the same as the operation mode of the air-conditioning apparatus 41 (YES in step S 304 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the third direction (step S 305 ). By contrast, when the controller 54 determines that the operation mode of the air-conditioning apparatus 40 is different from the operation mode of the air-conditioning apparatus 41 (NO in step S 304 ), the process proceeds to step S 306 .
  • step S 306 the controller 54 determines, on the basis of each operation information, whether the air-conditioning apparatus 40 is in thermo-on state and the air-conditioning apparatus 41 is in thermo-on state.
  • air-conditioning apparatus 40 is in thermo-on state
  • air-conditioning apparatus 41 is in thermo-on state
  • compressor (not illustrated) of the air-conditioning apparatus 41 is in operation.
  • step S 306 When determining in step S 306 that at least one of the air-conditioning apparatuses 40 and 41 is not in thermo-on state (NO in step S 306 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the third direction (step S 310 ). By contrast, when the controller 54 determines that the air-conditioning apparatuses 40 and 41 are both in thermo-on state (YES in step S 306 ), the process proceeds to step S 307 .
  • step S 307 the controller 54 determines, on the basis of each operation information, whether the ventilator 53 is in operation.
  • the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the third direction (step S 310 ).
  • the process proceeds to step S 308 .
  • step S 308 the controller 54 determines, on the basis of outside-air temperature information, whether the outside air temperature is higher than a first temperature set in advance and lower than a second temperature set in advance.
  • the first temperature is a low temperature threshold at which the operation of the refrigeration cycle becomes unstable
  • the second temperature is a high temperature threshold at which the operation of the refrigeration cycle becomes unstable.
  • step S 308 When determining in step S 308 that the outside air temperature is higher than the first temperature and lower than the second temperature (YES in step S 308 ), the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the second direction (step S 309 ).
  • the controller 54 determines that the outside air temperature is lower than or equal to the first temperature, or higher than or equal to the second temperature (NO in step S 308 )
  • the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the first direction (step S 311 ).
  • the controller 54 causes the second flow switching device 9 to switch the flow direction of the refrigerant to the second direction. Since the second flow switching device 9 is controlled in the above manner, exhaust heat from the air-conditioning apparatus 40 installed in the first space 101 can be used in the second space 102 . It is therefore possible to reduce the internal air-conditioning load in the second space 102 and improve the energy efficiency of the entire heat pump system 100 to achieve energy savings.
  • the second auxiliary heat exchanger 16 can be made to perform part of heat exchange that should be performed at the outdoor-side heat exchanger 5 of the air-conditioning apparatus 40 .
  • the flow rate of air to be sent by the outdoor fan 6 in the air-conditioning apparatus 40 can be reduced.
  • the rotation speed of the outdoor fan 6 can be reduced, it is possible to reduce noise and improve the energy efficiency to achieve energy savings.
  • the flow direction set by the second flow switching device 9 is not switched to the second direction.
  • priority is given to control of the ventilation. It is therefore hard to control the amount of air in the supply air passage 11 or the exhaust air passage 12 of the ventilator 53 in such a manner as to stabilize the operation of the refrigeration cycle.
  • the flow direction set by the second flow switching device 9 is switched to the first direction to give priority to stabilization of the operation of the refrigeration cycle.
  • FIG. 12 is a diagram illustrating an example of the second flow switching device 9 of the heat pump system 100 according to Embodiment 3 of the present disclosure.
  • FIG. 13 is a diagram illustrating another example of the second flow switching device 9 of the heat pump system 100 according to Embodiment 3 of the present disclosure.
  • FIGS. 12 and 13 each schematically illustrate the second flow switching device 9 as viewed in a direction along the rotation axis.
  • the second flow switching device 9 is, for example, a rotary valve having conductive portions, which are shaded as indicated in the figure, has a cylindrical shape, and includes an outer peripheral portion 80 and a cylindrical valve body 81 .
  • connection apertures 80 a to 80 d are formed, and in the cylindrical valve body 81 , a conduit 81 a formed.
  • connection aperture 80 a is connected with the outdoor-side heat exchanger 5 by a refrigerant pipe 1
  • connection aperture 80 b is connected with the first auxiliary heat exchanger 15 by a refrigerant pipe 1
  • connection aperture 80 c is connected with the second auxiliary heat exchanger 16 by a refrigerant pipe 1
  • connection aperture 80 d is connected with the expansion device 8 by a refrigerant pipe 1 .
  • the second flow switching device 9 is, for example, a rotary valve having conductive portions, which are shaded as indicated in the figure, has a cylindrical shape, and includes an outer peripheral portion 90 and a cylindrical valve body 91 .
  • connection apertures 90 a to 90 d are formed, and in the cylindrical valve body 91 , conduits 91 a to 91 c are formed.
  • FIG. 14 illustrates examples of the operation of the second flow switching device 9 of the heat pump system 100 according to Embodiment 3 of the present disclosure. Specifically, FIG. 14 indicates a list of advantages (achievable operation modes) that are obtained in the case where rotation angles of the rotary valves are rotation angles indicated in the figure. In this case, it is assumed that the rotation angles of the rotary valves that are set as illustrated in FIGS. 12 and 13 are each a reference angle (0 degrees).
  • the flow direction set by the second flow switching device 9 is the third direction, and the heat exchange at the outdoor-side heat exchanger 5 is assisted.
  • the flow direction set by the second flow switching device 9 is the first direction, and the refrigerant bypasses the first auxiliary heat exchanger 15 and the second auxiliary heat exchanger 16 installed inside the ventilator 53 .
  • the flow direction set by the second flow switching device 9 is the second direction, and the internal air-conditioning load in the second space 102 is reduced.
  • the flow direction set by the second flow switching device 9 is the third direction, and the heat exchange at the outdoor-side heat exchanger 5 is assisted.
  • the flow direction set by the second flow switching device 9 is the first direction, and the refrigerant bypasses the first auxiliary heat exchanger 15 and the second auxiliary heat exchanger 16 installed inside the ventilator 53 .
  • the flow direction set by the second flow switching device 9 is the second direction, and the internal air-conditioning load in the second space 102 is reduced.
  • the controller 54 causes the second flow switching device 9 to switch the flow passage for the refrigerant to the flow passage in which the refrigerant flows into the first auxiliary heat exchanger 15 , when the following first condition is satisfied: the operation mode of the air-conditioning apparatus 40 that air-conditions the first space 101 is different from that of the air-conditioning apparatus 41 that air-conditions the second space 102 ; the compressor 3 of the air-conditioning apparatus 40 and the compressor (not illustrated) of the air-conditioning apparatus 41 are both in operation, and the ventilator 53 is in operation.
  • the controller 54 when the first condition is satisfied and the outside air temperature is lower than or equal to the first temperature set in advance or higher than or equal to the second temperature set in advance and higher than the first temperature, the controller 54 causes the second flow switching device 9 to switch the flow passage for the refrigerant to the flow passage in which the refrigerant flows into the bypass 18 .
  • the heat pump system 100 according to Embodiment 3 can give priority to stabilization of the operation of the refrigeration cycle circuit.
  • Embodiment 4 of the present disclosure will be described. It should be noted that with respect to Embodiment 4, part of the above descriptions regarding Embodiments 1 to 3 that can also be applied to Embodiment 4 will not be repeated, and components that are the same as or equivalent to those in each of Embodiments 1 to 3 will be denoted by the same reference signs.
  • FIG. 15 is a first detailed configuration diagram of the heat pump system 100 according to Embodiment 4 of the present disclosure.
  • an auxiliary heat exchanger 25 is provided in part of the supply air passage 11 that is located between the total heat exchanger 10 and the supply air fan 13 .
  • the heat pump system 100 includes a refrigerant circuit in which the compressor 3 , the first flow switching device 4 , the indoor-side heat exchanger 7 , the expansion device 8 , and a water heat exchanger 22 are sequentially connected by refrigerant pipes 27 to allow refrigerant to circulate.
  • the heat pump system 100 also includes a water circuit in which the water heat exchanger 22 , a heat-source-side heat exchanger 23 , the auxiliary heat exchanger 25 , and a pump 26 are sequentially connected by a water pipe 28 to allow water to circulate.
  • a bypass open/close valve 24 is provided in parallel with the auxiliary heat exchanger 25 .
  • the water heat exchanger 22 causes refrigerant that flows in the refrigerant circuit to exchange heat with water that flows in the water circuit.
  • the bypass open/close valve 24 is connected to both ends of the auxiliary heat exchanger 25 by the water pipe 28 . When being in closed state, the bypass open/close valve 24 allows water to pass through the auxiliary heat exchanger 25 . By contrast, when being in opened state, the bypass open/close valve 24 does not allow water to pass through the auxiliary heat exchanger 25 .
  • the heat-source-side heat exchanger 23 causes water that flows in the water circuit to exchange heat with air that flows in the indoor space.
  • the auxiliary heat exchanger 25 causes air that has passed through the total heat exchanger 10 to exchange heat with water.
  • the auxiliary heat exchanger 25 is configured to cause air taken from the outdoor space into the ventilator 53 to pass through the total heat exchanger 10 and then pass through the auxiliary heat exchanger 25 . Because of this configuration, priority is given to heat exchange of air that flows in the indoor space. It is therefore possible to ensure the comfortability of the indoor space and improve the energy efficiency of the air-conditioning apparatus 40 to achieve energy savings.
  • FIG. 16 is a second detailed configuration diagram of the heat pump system 100 according to Embodiment 4 of the present disclosure.
  • the heat pump system 100 may be configured such that a plurality of refrigerant circuits and a plurality of water circuits are provided, and the water circuits are arranged in parallel with each other.
  • the heat pump system 100 may be configured such that a plurality of indoor-side heat exchangers 7 and a plurality of expansion devices 8 are provided, and the indoor-side heat exchangers 7 are arranged in parallel with the expansion devices 8 .
  • the second flow switching device 9 corresponds to “flow switching device” of the present disclosure
  • the air-conditioning apparatus 40 corresponds to “first air-conditioning apparatus” of the present disclosure
  • the air-conditioning apparatus 41 corresponds to “second air-conditioning apparatus” of the present disclosure.

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  • Combustion & Propulsion (AREA)
  • Signal Processing (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Air Conditioning Control Device (AREA)
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US16/640,084 2017-10-27 2017-10-27 Heat pump system Abandoned US20200200448A1 (en)

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Cited By (2)

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US11519632B2 (en) * 2020-10-16 2022-12-06 Richard T. Burks, III Variable air flow / multiple zone HVAC air terminal system
DE102022001816A1 (de) 2022-05-14 2023-11-16 Matthias Leipoldt Lüftungsanlage mit Heiz- und Kühlfunktion zur Beeinflussung der Raumluft wenigstens eines Raumes

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CN110220277B (zh) * 2019-06-11 2021-08-27 宁波奥克斯电气股份有限公司 一种空调器的控制方法、装置及空调器
KR20210098023A (ko) * 2020-01-31 2021-08-10 엘지전자 주식회사 공기조화기
JP7132526B2 (ja) * 2020-09-18 2022-09-07 ダイキン工業株式会社 追加換気装置および空気調和装置の選定方法、および、空調換気システム
JP2023007129A (ja) * 2021-07-01 2023-01-18 ダイキン工業株式会社 空気調和システム
JPWO2023058197A1 (ja) * 2021-10-07 2023-04-13
JP7280529B1 (ja) * 2021-12-17 2023-05-24 ダイキン工業株式会社 換気システム

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JPS5744273Y2 (ja) * 1978-05-23 1982-09-30
JPH0244142A (ja) * 1988-08-02 1990-02-14 Daikin Ind Ltd 室外空気処理装置
JPH10325589A (ja) * 1997-05-22 1998-12-08 Daikin Ind Ltd 熱回収型空気調和装置
JP2004271080A (ja) * 2003-03-10 2004-09-30 Tokyo Electric Power Co Inc:The 冷熱機器と温熱機器の統合機器
JP5068235B2 (ja) * 2008-10-28 2012-11-07 三菱電機株式会社 冷凍空調装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11519632B2 (en) * 2020-10-16 2022-12-06 Richard T. Burks, III Variable air flow / multiple zone HVAC air terminal system
DE102022001816A1 (de) 2022-05-14 2023-11-16 Matthias Leipoldt Lüftungsanlage mit Heiz- und Kühlfunktion zur Beeinflussung der Raumluft wenigstens eines Raumes

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