WO2021140589A1 - 空気調和装置 - Google Patents

空気調和装置 Download PDF

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Publication number
WO2021140589A1
WO2021140589A1 PCT/JP2020/000296 JP2020000296W WO2021140589A1 WO 2021140589 A1 WO2021140589 A1 WO 2021140589A1 JP 2020000296 W JP2020000296 W JP 2020000296W WO 2021140589 A1 WO2021140589 A1 WO 2021140589A1
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WO
WIPO (PCT)
Prior art keywords
user
heat medium
heat
valve
cooling
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/JP2020/000296
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
宗史 池田
淳 西尾
直史 竹中
亮宗 石村
祐治 本村
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to US17/775,313 priority Critical patent/US12061019B2/en
Priority to PCT/JP2020/000296 priority patent/WO2021140589A1/ja
Priority to JP2021569647A priority patent/JP7301166B2/ja
Priority to EP20911699.5A priority patent/EP4089336A4/en
Publication of WO2021140589A1 publication Critical patent/WO2021140589A1/ja
Anticipated expiration legal-status Critical
Ceased 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
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F24D19/1039—Arrangement or mounting of control or safety devices for water heating systems for central heating the system uses a heat pump
    • 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
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line 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
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • F25B21/00—Machines, plants or systems, using electric or magnetic effects
    • F25B21/02—Machines, plants or systems, using electric or magnetic effects using Peltier effect; using Nernst-Ettinghausen effect
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02791—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using shut-off 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/029—Control issues
    • F25B2313/0292—Control issues related to reversing 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/12—Inflammable refrigerants
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/16—Receivers
    • 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
    • F25B2700/2103—Temperatures near a 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • This technology is related to air conditioners.
  • the present invention relates to an air conditioner having a configuration in which a phase-changing heat medium is conveyed by a pump.
  • a circuit that constitutes a primary side cycle (hereinafter, referred to as a primary side cycle) and a circuit that constitutes a secondary side cycle (hereinafter, referred to as a secondary side cycle) are used in phase.
  • An air conditioner using a refrigerant with a change is known.
  • the primary side cycle is composed of a vapor compression type cycle circuit and the secondary side cycle is composed of a liquid pump cycle circuit (see, for example, Patent Document 1).
  • This air conditioner cools the air by absorbing the heat in the room in the secondary cycle.
  • the refrigerant of the primary side cycle absorbs heat from the refrigerant of the secondary side cycle through the heat exchanger that exchanges heat between the refrigerants of each cycle. Then, in the primary side cycle, the heat of the refrigerant in the primary side cycle is radiated to the outside to realize air conditioning that cools the air conditioning target space.
  • the air conditioner having the configuration of Patent Document 1 can perform a cooling operation of absorbing heat in a room which is an air conditioning target space and cooling the air, but performs a heating operation of radiating heat to the room and heating the air. Can't. Therefore, the refrigerant in the primary cycle cannot heat the refrigerant in the secondary cycle. Further, even if the refrigerant of the primary side cycle can heat the refrigerant of the secondary side cycle, gas flows into the pump of the secondary side cycle due to the configuration of the secondary side cycle. If gas flows into the pump, the drive may become unstable or malfunction. Therefore, the air conditioner having the configuration as in Patent Document 1 has a problem that the heating operation cannot be performed.
  • the purpose is to obtain an air conditioner capable of performing stable air conditioning operation.
  • the air conditioner disclosed here exchanges heat between a heat source side heat medium and a user side heat medium different from the heat source side heat medium, and absorbs or dissipates heat to the heat source side heat medium by switching to phase the user side heat medium.
  • the air in the space to be air-conditioned is heated by a heat source side device having a changing intermediate heat exchanger, an intermediate heat exchanger, a pump that sucks in and sends out a liquid utilization side heat medium, and heat exchange that accompanies a phase change of the utilization side heat medium.
  • a user-side heat exchanger for cooling and a user-side cycle circuit for circulating the user-side heat medium by connecting a decompression device for reducing the pressure of the user-side heat medium passing through the user-side heat exchanger with a pipe.
  • This air conditioner drives a pump, heats or cools the heat medium on the user side in the intermediate heat exchanger to change the phase, and efficiently heats or cools the air in the space to be air-conditioned by the heat exchanger on the user side. Harmony can be done.
  • the pump since the pump sucks in the liquid heat medium for use and sends it out, it is possible to suppress the gas-like heat medium for use from passing through the pump and perform stable heating and cooling operation.
  • FIG. It is a figure which typically described an example of the structure of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a figure explaining the flow of the heat medium at the time of cooling operation and heating operation of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a figure which typically described an example of the structure of the air conditioner which concerns on Embodiment 2.
  • FIG. It is a figure explaining the flow of the heat medium at the time of cooling operation and heating operation of the air conditioner which concerns on Embodiment 2.
  • FIG. It is a figure explaining the flow of the utilization side heat medium in the receiver, and the state of the utilization side heat medium at the time of cooling operation and heating operation of the air conditioner which concerns on Embodiment 2.
  • FIG. 5 is a diagram schematically showing an example of the configuration of an air conditioner according to a fifth embodiment. It is a figure explaining the flow of the heat medium at the time of a cooling operation and a heating operation of the air conditioner of Embodiment 5.
  • the air conditioner according to the embodiment will be described with reference to drawings and the like.
  • those having the same reference numerals are the same or equivalent thereto, and are common to the whole texts of the embodiments described below.
  • the relationship between the sizes of the constituent members may differ from the actual one.
  • the form of the component represented in the entire specification is merely an example, and is not limited to the form described in the specification.
  • the combination of components is not limited to the combination in each embodiment, and the components described in other embodiments can be applied to other embodiments.
  • the height of pressure, temperature, etc. is not determined in relation to the absolute value, but is relatively determined in the state, operation, etc. of the device or the like. Then, when it is not necessary to particularly distinguish or specify a plurality of devices of the same type that are distinguished by subscripts, the subscripts and the like may be omitted.
  • FIG. 1 is a diagram schematically showing an example of the configuration of the air conditioner according to the first embodiment.
  • the air conditioner 100 is configured by connecting the outdoor unit 101 and a plurality of indoor units 102 (indoor unit 102a and indoor unit 102b) with an outward pipe 81a and a return pipe 81b.
  • the air conditioner 100 in which the outdoor unit 101 and the plurality of indoor units 102 are connected by piping has a heat source side cycle circuit (hereinafter, referred to as a heat source side cycle 110) by a primary side heat pump through which a heat source side heat medium circulates.
  • the heat source side cycle 110 serves as a heat source side device.
  • a user-side cycle circuit (hereinafter referred to as a user-side cycle 120) by a user-side heat pump in which a user-side heat medium circulates.
  • the heat source side heat medium in the heat source side cycle 110 circulates only inside the outdoor unit 101.
  • the heat medium on the user side in the cycle 120 on the user side circulates in the order of the outdoor unit 101, the forward pipe 81a, the indoor unit 102, and the return pipe 81b.
  • the air conditioner 100 of FIG. 1 shows an example of having two indoor units 102a and an indoor unit 102b, but the present invention is not limited to two, and one or three or more indoor units 102. It may have.
  • the outdoor unit 101 is, for example, a device installed outside a room that is a space subject to air conditioning, and dissipates heat related to air conditioning to the outside or absorbs heat from the outside.
  • the outdoor unit 101 includes a compressor 1, a heat source side flow path switching device 2, a heat source side heat exchanger 3, a drawing device 4, an intermediate heat exchanger 5, and an accumulator 6, which are elements of the heat source side cycle 110. Further, the outdoor unit 101 is equipped with a heat source side fan 10 that blows air to the heat source side heat exchanger 3.
  • the outdoor unit 101 includes a pump 51, a first on-off valve 54a for cooling, a second on-off valve 54b for cooling, a third on-off valve 54c for cooling, and a first on-off valve 55a for heating, which are elements of the cycle 120 on the user side. It is equipped with a second on-off valve 55b for heating and a third on-off valve 55c for heating.
  • the indoor unit 102 is, for example, a device installed inside a room to dissipate heat related to air conditioning into the room or absorb heat from the room.
  • the indoor unit 102 is equipped with a user-side heat exchanger 52 and a decompression device 53, which are devices for the user-side cycle 120. Further, the indoor unit 102 is equipped with a user-side fan 60. Therefore, the indoor unit 102a is equipped with a user-side heat exchanger 52a, a decompression device 53a, and a user-side fan 60a. Further, the indoor unit 102b is equipped with a heat exchanger 52b on the user side, a decompression device 53b, and a fan 60b on the user side.
  • the compressor 1 is a device composed of, for example, an inverter compressor whose capacity can be controlled, and which sucks in a low-pressure heat source-side heat medium, compresses it, and discharges it at a high pressure.
  • the heat source side flow path switching device 2 is composed of, for example, a four-way valve, and is a device that switches between a flow path in a cooling operation and a flow path in a heating operation to switch a heat exchanger that acts as a condenser and an evaporator. Is.
  • the compressor 1, the heat source side flow path switching device 2, the heat source side heat exchanger 3, the drawing device 4, and the intermediate heat exchanger 5 are switched by switching the heat source side flow path switching device 2.
  • the heat source side flow path switching device 2, the accumulator 6, and the compressor 1 are connected in this order.
  • the heat source side heat exchanger 3 acts as a condenser
  • the intermediate heat exchanger 5 acts as an evaporator.
  • the compressor 1, the heat source side flow path switching device 2, the intermediate heat exchanger 5, the drawing device 4, and the heat source side heat exchanger are switched by switching the heat source side flow path switching device 2. 3.
  • the heat source side flow path switching device 2, the accumulator 6 and the compressor 1 are connected in this order. Then, the heat source side heat exchanger 3 acts as an evaporator, and the intermediate heat exchanger 5 acts as a condenser.
  • the present invention is not limited to the four-way valve, and a three-way valve or a combination of two-way valves may be used. It may be applied as a heat source side flow path switching device 2.
  • the heat source side heat exchanger 3 is a device that exchanges heat between the air supplied from the heat source side fan 10 and the heat source side heat medium.
  • the heat source side heat exchanger 3 is composed of, for example, a fin tube type heat exchanger or the like. One end of the heat source side heat exchanger 3 is connected to the heat source side flow path switching device 2, and the other end is connected to the throttle device 4.
  • the heat source side heat exchanger 3 during the cooling operation acts as a condenser by radiating heat from the high temperature heat source side heat medium to air having a lower temperature than the heat source side heat medium.
  • the heat source side heat exchanger 3 during the heating operation acts as an evaporator by absorbing heat from the air having a higher temperature than the heat source side heat medium by the low temperature heat source side heat medium.
  • a fin tube type heat exchanger is applied as the heat source side heat exchanger 3
  • the present invention is not limited to the fin tube type heat exchanger, and the plate type heat exchanger is not limited to the fin tube type heat exchanger. Etc. may be applied.
  • the drawing device 4 is a device that reduces the pressure of the heat medium on the heat source side.
  • the throttle device 4 is composed of, for example, an electronic expansion valve or the like whose opening degree can be variably controlled.
  • One end of the drawing device 4 is connected to the heat source side heat exchanger 3, and the other end is connected to the intermediate heat exchanger 5.
  • an electronic expansion valve is applied as the throttle device 4
  • a capillary tube, an electromagnetic valve, or the like may be applied. ..
  • the intermediate heat exchanger 5 is a device that exchanges heat between the heat source side heat medium that circulates in the heat source side cycle 110 and the user side heat medium that circulates in the user side cycle 120.
  • the intermediate heat exchanger 5 is composed of, for example, a plate heat exchanger or the like.
  • one end of the flow path on the heat source side cycle 110 side is connected to the throttle device 4, and the other end of the flow path on the heat source side cycle 110 side is connected to the heat source side flow path switching device 2.
  • one end of the flow path on the utilization side cycle 120 side is connected to the return pipe 81b, and the other end of the flow path on the utilization side cycle 120 side is connected to the pump 51.
  • the intermediate heat exchanger 5 during the cooling operation acts as an evaporator. Therefore, the low-temperature heat source-side heat medium absorbs heat from the utilization-side heat medium having a higher temperature than the heat-source-side heat medium. Further, the intermediate heat exchanger 5 during the heating operation acts as a condenser. Therefore, the high-temperature heat source-side heat medium dissipates heat to the lower-temperature utilization-side heat medium than the heat source-side heat medium.
  • a plate heat exchanger is applied as the intermediate heat exchanger 5 will be shown, but the present invention is not limited to the plate heat exchanger, and is not limited to the plate heat exchanger, such as a double tube heat exchanger. May be applied.
  • the accumulator 6 is a difference between a heating operation and a cooling operation, and stores a surplus heat source side heat medium generated in the heat source side cycle 110 or a surplus heat source side heat medium generated by a transitional change in operation.
  • One end of the accumulator 6 is connected to the heat source side flow path switching device 2, and the other end is connected to the compressor 1.
  • the present invention is not limited to the accumulator 6, and a receiver or the like may be applied.
  • the pump 51 is a device that sucks in a liquid heat medium on the user side, raises the pressure, and sends it out.
  • the pump 51 is, for example, an inverter type centrifugal pump or a turbo type non-volumetric pump.
  • the user-side heat exchanger 52 (user-side heat exchanger 52a and user-side heat exchanger 52b) connects the air supplied from the user-side fan 60 (user-side fan 60a and user-side fan 60b) with the user-side heat medium. It is a device that exchanges heat.
  • the user-side heat exchanger 52 is composed of, for example, a fin tube type heat exchanger.
  • the user-side heat exchanger 52 is connected to the outgoing pipe 81a, and the other end is connected to the decompression device 53 (decompression device 53a and decompression device 53b).
  • the user-side heat exchanger 52 during the cooling operation acts as an evaporator. Therefore, the low-temperature user-side heat medium absorbs heat from the air having a higher temperature than the user-side heat medium and cools the air. Further, the heat exchanger 52 on the user side during the heating operation acts as a condenser. Therefore, the high-temperature user-side heat medium dissipates heat to air at a lower temperature than the user-side heat medium, and heats the air.
  • a fin tube type heat exchanger is applied as the user side heat exchanger 52
  • the present invention is not limited to the fin tube type heat exchanger
  • the plate type heat exchanger is not limited to the fin tube type heat exchanger. Etc. may be applied.
  • the decompression device 53 (decompression device 53a and decompression device 53b) is a device that depressurizes the passing heat medium on the utilization side.
  • the pressure reducing device 53 is composed of, for example, an electronic expansion valve or the like whose opening degree can be variably controlled.
  • One end of the decompression device 53 is connected to the user side heat exchanger 52 (the user side heat exchanger 52a and the user side heat exchanger 52b), and the other end is connected to the return pipe 81b.
  • an electronic expansion valve is applied as the pressure reducing device 53 will be shown, but the present invention is not limited to the electronic expansion valve, and a capillary tube or the like may be applied.
  • the first on-off valve 54a for cooling, the second on-off valve 54b for cooling, the third on-off valve 54c for cooling, the first on-off valve 55a for heating, the second on-off valve 55b for heating, and the third on-off valve 55c for heating are cooled. It is a valve that switches between the flow path in operation and the flow path in heating operation. These on-off valves serve as a utilization-side flow path switching device that switches the flow path of the utilization-side cycle 120.
  • the valve when the valve is not specified, it may be described as a cooling on-off valve 54 and a heating on-off valve 55.
  • the on-off valve 54 for cooling and the on-off valve 55 for heating switch a heat exchanger that acts as a condenser and an evaporator by switching the flow path.
  • the cooling on-off valve 54 and the heating on-off valve 55 are composed of valves that can be opened and closed, such as a solenoid valve.
  • the utilization side cycle 120 includes a pump 51, a second on-off valve for cooling 54b, an outward pipe 81a, a heat exchanger 52 on the utilization side, a pressure reducing device 53, a return pipe 81b, a third on-off valve for cooling 54c, and intermediate heat. It serves as a flow path for the exchanger 5, the first on-off valve 54a for cooling, and the pump 51.
  • the intermediate heat exchanger 5 acts as a condenser
  • the user side heat exchanger 52 acts as an evaporator.
  • the user-side cycle 120 includes a pump 51, a second on-off valve for heating 55b, an intermediate heat exchanger 5, a third on-off valve for heating 55c, an outgoing pipe 81a, a heat exchanger 52 on the user-side, and a decompression device 53. It serves as a flow path for the return pipe 81b, the first on-off valve 55a for heating, and the pump 51.
  • the intermediate heat exchanger 5 acts as an evaporator
  • the user side heat exchanger 52 acts as a condenser.
  • a solenoid valve is applied as the cooling on-off valve 54 and the heating on-off valve 55
  • the present invention is not limited to the solenoid valve, and a three-way valve and a two-way valve are combined. Equipment and the like may be applied.
  • the first on-off valve 54a for cooling is a valve that opens and closes the flow path connecting the intermediate heat exchanger 5 and the pump 51.
  • One end of the cooling first on-off valve 54a is connected to the intermediate heat exchanger 5, and the other end is connected to the pump 51.
  • the first on-off valve 54a for cooling during the cooling operation opens the flow path connecting the intermediate heat exchanger 5 and the pump 51 by opening. Further, the first on-off valve 54a for cooling during the heating operation is closed to shut off the flow paths of the intermediate heat exchanger 5 and the pump 51.
  • the second on-off valve 54b for cooling is a valve that opens and closes the flow path connecting the pump 51 and the outgoing pipe 81a.
  • One end of the cooling second on-off valve 54b is connected to the pump 51, and the other end is connected to the outgoing pipe 81a.
  • the second on-off valve 54b for cooling during the cooling operation opens the flow path connecting the pump 51 and the outgoing pipe 81a by opening. Further, the second on-off valve 54b for cooling during the heating operation shuts off the flow path of the pump 51 and the outgoing pipe 81a by closing.
  • the third on-off valve 54c for cooling is a valve that opens and closes the flow path connecting the return pipe 81b and the intermediate heat exchanger 5.
  • One end of the cooling third on-off valve 54c is connected to the return pipe 81b, and the other end is connected to the intermediate heat exchanger 5.
  • the third on-off valve 54c for cooling during the cooling operation opens the flow path connecting the return pipe 81b and the intermediate heat exchanger 5 by opening. Further, the third on-off valve 54c for cooling during the heating operation shuts off the flow path of the return pipe 81b and the intermediate heat exchanger 5 by closing.
  • the first on-off valve 55a for heating is a valve that opens and closes the flow path connecting the return pipe 81b and the pump 51.
  • the first on-off valve 55a for heating is arranged on a pipe connecting the return pipe 81b and the third on-off valve 54c for cooling and the pipe between the first on-off valve 54a for cooling and the pump 51. It is installed.
  • the first on-off valve 55a for heating during the cooling operation shuts off the flow path connecting the return pipe 81b and the pump 51 by closing. Further, the first on-off valve 55a for heating during the heating operation opens the flow paths of the intermediate heat exchanger 5 and the pump 51 by opening.
  • the second on-off valve 55b for heating is a valve that opens and closes the flow path connecting the pump 51 and the intermediate heat exchanger 5.
  • the second on-off valve 55b for heating is on a pipe connecting the pipe between the pump 51 and the second on-off valve 54b for cooling and the pipe between the third on-off valve 54c for cooling and the intermediate heat exchanger 5. It is arranged in.
  • the second on-off valve 55b for heating during the cooling operation shuts off the flow path connecting the pump 51 and the intermediate heat exchanger 5 by closing. Further, the second on-off valve 55b for heating during the heating operation opens the flow paths of the pump 51 and the intermediate heat exchanger 5 by opening.
  • the third on-off valve 55c for heating is a valve that opens and closes the flow path connecting the intermediate heat exchanger 5 and the outgoing pipe 81a.
  • the third on-off valve 55c for heating is a pipe that connects the pipe between the intermediate heat exchanger 5 and the first on-off valve 54a for cooling and the pipe between the second on-off valve 54b for cooling and the outgoing pipe 81a. Arranged on top. By closing the third on-off valve 55c for heating during the cooling operation, the flow path connecting the intermediate heat exchanger 5 and the outgoing pipe 81a is cut off. Further, the second on-off valve 55b for heating during the heating operation opens the flow path of the intermediate heat exchanger 5 and the forward pipe 81a by opening.
  • the forward pipe 81a and the return pipe 81b are pipes that connect the outdoor unit 101 and the indoor unit 102 to form a flow path for the user-side cycle 120.
  • the forward pipe 81a and the return pipe 81b are made of, for example, a copper pipe.
  • One end of the outgoing pipe 81a is connected to the second on-off valve 54b for cooling and the third on-off valve 55c for heating, and the other end is connected to the heat exchanger 52 on the utilization side.
  • one end of the return pipe 81b is connected to the pressure reducing device 53, and the other end is connected to the cooling third on-off valve 54c.
  • the heat source side heat medium that circulates in the heat source side cycle 110 is a medium that mainly conveys the heat exchanged between the outdoor air and the utilization side heat medium.
  • the heat source side heat medium used in the first embodiment is, for example, a refrigerant for an air conditioner such as R32.
  • R32 refrigerant for an air conditioner such as R32.
  • the heat source side heat medium may be R1123, R1132 (E), R1234yf, R1234ze (E), R1234ze (Z), R290, or a refrigerant in which they are mixed.
  • the user-side heat medium that circulates in the user-side cycle 120 is mainly a refrigerant that carries the heat exchanged between the indoor air and the user-side heat medium.
  • the utilization-side heat medium used in the first embodiment is, for example, a nonflammable air conditioner refrigerant such as R466A.
  • R466A refrigerant such as R466A.
  • the heat medium on the utilization side may be R134a, R1233zd (E), R1243zf, R1216, R1336mzz (Z), R13I1, R744, or a nonflammable refrigerant in which they are mixed.
  • the control device 91 operates the entire air conditioner based on detection signals from various sensors (not shown) installed in the outdoor unit 101, the indoor unit 102, and the like, operation signals from the operation unit (not shown), and the like. To control. In particular, the control device 91 controls the drive of actuators such as the compressor 1, the throttle device 4, the heat source side fan 10, the pump 51, and the user side fan 60.
  • the control device 91 includes a microcomputer provided with a CPU (Central Processing Unit), a ROM (Read Only Memory), a RAM (Random Access Memory), an I / O port, and the like.
  • a CPU Central Processing Unit
  • ROM Read Only Memory
  • RAM Random Access Memory
  • control device 91 will be described as being installed in the outdoor unit 101, but the installation location of the control device 91 is not particularly limited.
  • the control device 91 may be provided in either the indoor unit 102a or the indoor unit 102b. Further, the control device 91 may be installed independently of the outdoor unit 101 or the like.
  • FIG. 2 is a diagram for explaining the flow of the heat medium during the cooling operation and the heating operation of the air conditioner according to the first embodiment.
  • the solid line and the broken line in FIG. 2 show the flow of the heat medium during the cooling operation and the heating operation, respectively.
  • the flow of the heat medium as well as the operation of each device will be described.
  • the pressure at which the saturation temperature is higher than that of the outdoor air is defined as the high pressure.
  • the pressure at which the saturation temperature is lower than that of the indoor air is defined as low pressure.
  • the compressor 1 compresses the sucked low-pressure gaseous heat source-side heat medium and discharges the high-pressure gaseous heat source-side heat medium.
  • the high-pressure gaseous heat source-side heat medium flows into the heat source-side heat exchanger 3 via the heat source-side flow path switching device 2.
  • the heat source side heat exchanger 3 cools a high-pressure gaseous heat source side heat medium with outdoor air supplied from the heat source side fan 10 to condense it.
  • the high-pressure liquid heat source-side heat medium condensed and liquefied by the heat-source-side heat exchanger 3 flows into the drawing device 4.
  • the drawing device 4 decompresses the high-pressure liquid heat source-side heat medium.
  • the low-pressure, two-phase heat source-side heat medium decompressed by the drawing device 4 flows into the intermediate heat exchanger 5.
  • the intermediate heat exchanger 5 exchanges heat between a low-pressure two-phase heat source-side heat medium and a user-side heat medium that circulates in the user-side cycle 120.
  • the low-pressure two-phase heat source-side heat medium is heated and evaporates and vaporizes.
  • the low-pressure gaseous heat source-side heat medium evaporated and vaporized by the intermediate heat exchanger 5 is sucked into the compressor 1 again via the heat source-side flow path switching device 2 and the accumulator 6.
  • the pressure at which the pressure is lower than the indoor air and the saturation temperature is higher than the low pressure saturation temperature of the heat source side heat medium is defined as the intermediate temperature. ..
  • the pump 51 boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature flows into the utilization-side heat exchanger 52 via the second on-off valve 54b for cooling and the forward pipe 81a.
  • the user-side heat exchanger 52 heats a liquid user-side heat medium having an intermediate temperature and vaporizes it by evaporating it by exchanging heat with the indoor air supplied from the user-side fan 60.
  • the gas-like heat medium of intermediate temperature vaporized by the heat exchanger 52 on the user side flows into the intermediate heat exchanger 5 via the pressure reducing device 53, the return pipe 81b, and the third on-off valve 54c for cooling. ..
  • the intermediate heat exchanger 5 exchanges heat between a gaseous heat medium on the utilization side at an intermediate temperature and a heat medium on the heat source side that circulates in the heat source side cycle 110.
  • the gas-like heat medium on the utilization side at an intermediate temperature is cooled and condensed.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure condensed by the intermediate heat exchanger 5 is sucked into the pump 51 again via the first on-off valve 54a for cooling.
  • the heat medium on the utilization side dissipates heat to the heat medium on the heat source side and absorbs heat from the indoor air. Therefore, the temperature relationship is such that the indoor air temperature> the saturation temperature of the heat medium on the utilization side> the low-pressure saturation temperature of the heat medium on the heat source side.
  • the pressure at which the saturation temperature is higher than that of the indoor air is defined as the high pressure. Further, the pressure at which the saturation temperature is lower than that of the outdoor air is defined as the low pressure.
  • the compressor 1 compresses the sucked low-pressure gaseous heat source-side heat medium and discharges the high-pressure gaseous heat source-side heat medium.
  • the high-pressure gaseous heat source-side heat medium flows into the intermediate heat exchanger 5 via the heat source-side flow path switching device 2.
  • the intermediate heat exchanger 5 exchanges heat between a high-pressure gaseous heat source-side heat medium and a user-side heat medium that circulates in the user-side cycle 120.
  • the high-pressure gaseous heat source-side heat medium is cooled and condensed.
  • the high-pressure liquid heat source-side heat medium condensed and liquefied by the intermediate heat exchanger 5 flows into the drawing device 4.
  • the drawing device 4 decompresses the high-pressure liquid heat source-side heat medium.
  • the low-pressure, two-phase heat source-side heat medium decompressed by the drawing device 4 flows into the heat-source-side heat exchanger 3.
  • the heat source side heat exchanger 3 heats a low-pressure two-phase heat source side heat medium with the outdoor air supplied from the heat source side fan 10 and evaporates and vaporizes it.
  • the low-pressure gaseous heat source-side heat medium evaporated and vaporized by the heat-source-side heat exchanger 3 is sucked into the compressor 1 again via the heat source-side flow path switching device 2 and the accumulator 6.
  • the pressure at which the pressure is higher than the indoor air and the saturation temperature is lower than the high-pressure saturation temperature of the heat source-side heat medium is defined as the intermediate temperature. ..
  • the pump 51 boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure flows into the intermediate heat exchanger 5 via the second on-off valve 55b for heating.
  • the intermediate heat exchanger 5 exchanges heat between a liquid utilization-side heat medium having an intermediate temperature and a heat source-side heat medium that circulates in the heat source-side cycle 110.
  • the liquid utilization side heat medium at intermediate temperature is heated and evaporates and vaporizes.
  • the gas-like heat medium on the utilization side having an intermediate temperature and vaporization vaporized by the intermediate heat exchanger 5 flows into the heat exchanger 52 on the utilization side via the third on-off valve 55c for heating and the outgoing pipe 81a.
  • the user-side heat exchanger 52 cools the gas-like user-side heat medium at an intermediate temperature and turns it into a condenser by heat exchange with the indoor air supplied from the user-side fan 60.
  • the liquid utilization-side heat medium having an intermediate temperature and liquefied by the utilization-side heat exchanger 52a is sucked into the pump 51 again via the heating first on-off valve 55a.
  • the control device 91 controls each device so that the heat medium on the user side in the user cycle 120 during the heating operation has a higher temperature and higher pressure than the heat medium on the user side in the user cycle 120 during the cooling operation. To do.
  • the evaporation temperature of the utilization side heat medium during the heating operation of the intermediate heat exchanger 5 is higher than the condensation temperature of the utilization side heat medium during the cooling operation, and the heating operation of the utilization side heat exchanger 52
  • the condensation temperature at the time is controlled to be higher than the evaporation temperature of the heat medium on the utilization side during the cooling operation.
  • the air conditioner 100 of the first embodiment drives a pump 51 that sucks in and sends out a liquid heat medium for use in the user cycle 120, and heats or cools the heat medium for use in the intermediate heat exchanger 5.
  • the phase is changed and the heat exchanger 52 is sent to the user side.
  • the user-side heat exchanger 52 heats or cools the air in the air-conditioned space to perform air conditioning.
  • the air conditioner 100 performs cooling operation and heating operation using a heat medium on the utilization side with a phase change, so that the capacity per unit flow rate is higher than that when a heat medium without a phase change such as water is used. Can be raised. Therefore, the air conditioner 100 can efficiently heat and cool the room.
  • the user side flow path switching device is configured to switch the flow path of the user side cycle 120 between the cooling operation and the heating operation. Therefore, the air conditioner 100 can switch between the cooling operation and the heating operation in response to the operation request from the indoor unit 102.
  • the pump 51 has a flow path in which the direction in which the heat medium on the user side flows in and out is the same, so that the heat medium on the user side is passed through the liquid and the heat medium on the user side is gaseous. Can be suppressed from passing through. Therefore, it is possible to prevent the occurrence of air biting in which the electric motor of the pump 51 runs idle, and to avoid a failure of the pump 51.
  • a third on-off valve 55c for heating was installed.
  • the control device 91 opens the first on-off valve 54a for cooling, the second on-off valve 54b for cooling, and the third on-off valve 54c for cooling to allow the heat medium on the user side to pass through.
  • control device 91 opens the first on-off valve 55a for heating, the second on-off valve 55b for heating, and the third on-off valve 55c for heating to pass the heat medium on the user side. Therefore, the flow path can be switched efficiently by blocking the flow path more reliably.
  • the air conditioner 100 of the first embodiment by using the heat medium that changes the phase, it is possible to realize the miniaturization of the pump 51, the thinning of the piping, and the improvement of the efficiency of the system. Further, since the air conditioner 100 uses a nonflammable heat medium as the heat medium on the user side, it is not necessary to install safety measures equipment necessary for reducing the risk of ignition at the time of leakage. Then, the utilization-side heat medium circulating in the utilization-side cycle 120 does not reach a temperature higher than the room temperature during the cooling operation and does not reach a temperature higher than the temperature of the heat source-side heat medium during the heating operation. Therefore, it is possible to suppress the decomposition reaction of the heat medium and the refrigerating machine oil due to the temperature rise.
  • FIG. 3 is a diagram schematically showing an example of the configuration of the air conditioner according to the second embodiment.
  • devices and the like having the same configuration as the air conditioner 100 of FIG. 1 are designated by the same reference numerals.
  • the air conditioner 100 of FIG. 3 has a different configuration of the outdoor unit 101.
  • the outdoor unit 101 of the second embodiment is equipped with a receiver 56 as an element of the user-side cycle 120.
  • the receiver 56 stores the surplus utilization side heat medium generated by the difference between the heating operation and the cooling operation or the surplus utilization side heat medium generated by the transitional change in operation. Further, the receiver 56 of the second embodiment suppresses the inflow of the gaseous heat medium on the utilization side into the pump 51.
  • the receiver 56 is connected at one end downstream from the confluence of the pipe connecting the first on-off valve 54a for cooling and the pump 51 and the pipe on which the first on-off valve 55a for heating is arranged, and the other end is the pump. It is connected to 51.
  • a configuration in which the air conditioner 100 has a receiver 56 is shown as an example, but a configuration having a gas-liquid separator or the like may be used instead of the receiver 56.
  • FIG. 4 is a diagram for explaining the flow of the heat medium during the cooling operation and the heating operation of the air conditioner according to the second embodiment.
  • the solid line and the broken line in FIG. 4 show the flow of the heat medium during the cooling operation and the heating operation, respectively.
  • the flow of the heat medium as well as the operation of each device will be described.
  • the flow of the heat source side heat medium and the operation of the equipment in the heat source side cycle 110 in the cooling operation and the heating operation are the same as those described in the first embodiment.
  • the pump 51 boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature flows into the utilization-side heat exchanger 52 via the second on-off valve 54b for cooling and the forward pipe 81a.
  • the user-side heat exchanger 52 heats a liquid user-side heat medium having an intermediate temperature and vaporizes it by evaporating it by exchanging heat with the indoor air supplied from the user-side fan 60.
  • the gas-like heat medium of intermediate temperature vaporized by the heat exchanger 52 on the user side flows into the intermediate heat exchanger 5 via the pressure reducing device 53, the return pipe 81b, and the third on-off valve 54c for cooling. ..
  • the intermediate heat exchanger 5 exchanges heat between a gaseous heat medium on the utilization side at an intermediate temperature and a heat medium on the heat source side that circulates in the heat source side cycle 110.
  • the gas-like heat medium on the utilization side at an intermediate temperature is cooled and condensed.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure condensed by the intermediate heat exchanger 5 is sucked into the pump 51 again via the first on-off valve 54a for cooling and the receiver 56.
  • the pump 51 boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure flows into the intermediate heat exchanger 5 via the second on-off valve 55b for heating.
  • the intermediate heat exchanger 5 exchanges heat between a liquid utilization-side heat medium having an intermediate temperature and a heat source-side heat medium that circulates in the heat source-side cycle 110.
  • the liquid utilization side heat medium at intermediate temperature is heated and evaporates and vaporizes.
  • the gas-like heat medium on the utilization side having an intermediate temperature and vaporization vaporized by the intermediate heat exchanger 5 flows into the heat exchanger 52 on the utilization side via the third on-off valve 55c for heating and the outgoing pipe 81a.
  • the user-side heat exchanger 52 cools the gas-like user-side heat medium at an intermediate temperature and turns it into a condenser by heat exchange with the indoor air supplied from the user-side fan 60.
  • the liquid utilization-side heat medium having an intermediate temperature and liquefied by the utilization-side heat exchanger 52a is sucked into the pump 51 again via the heating first on-off valve 55a and the receiver 56.
  • FIG. 5 is a diagram for explaining the flow of the heat medium on the user side and the state of the heat medium on the user side in the receiver during the cooling operation and the heating operation of the air conditioner according to the second embodiment.
  • the solid line and the broken line in FIG. 5 show the flow of the heat medium during the cooling operation and the heating operation, respectively.
  • the white outline and the colored coating in the receiver 56 of FIG. 5 indicate a gaseous heat medium for use side and a liquid heat medium for use side, respectively.
  • the flow direction of the heat medium on the utilization side is the same in the heating operation and the cooling operation.
  • the two-phase heat medium on the utilization side that has flowed into the receiver 56 from the inlet has a reduced flow rate in the container of the receiver 56.
  • the low-density gaseous heat medium for use is moved to the upper part, and the high-density liquid heat medium for use is moved to the bottom, so that the gas-like heat medium for use and the liquid heat medium for use are liquid in the container.
  • the present invention is not limited to the two-phase heat medium for use side, and a liquid heat medium for use side is used for the receiver 56. It may flow in.
  • the receiver 56 is installed in the utilization side cycle 120 to separate the gaseous utilization side heat medium and the liquid utilization side heat medium and pass them through the liquid utilization side heat medium. I did. Therefore, as compared with the first embodiment, the pump 51 can be configured so that the gaseous heat medium on the utilization side does not flow into the pump 51. Therefore, the failure of the pump 51 can be avoided.
  • FIG. 6 is a diagram schematically showing an example of the configuration of the air conditioner according to the third embodiment.
  • the same reference numerals are given to devices and the like having the same configuration as the air conditioner 100 of FIG.
  • the air conditioner 100 of FIG. 6 has a different configuration of the outdoor unit 101.
  • the outdoor unit 101 of the third embodiment is equipped with a decomposition product precipitation device 57 and an intermediate heat exchanger outlet temperature sensor 92 in the utilization side cycle 120.
  • the decomposition product precipitation device 57 is a device having a structure in which the receiver 56 described in the second embodiment includes a cooling device 58.
  • the cooling device 58 stores the surplus utilization side heat medium generated by the difference between the heating operation and the cooling operation or the surplus utilization side heat medium generated by the transitional change in operation.
  • the decomposition product precipitation device 57 of the third embodiment suppresses the inflow of the gaseous heat medium on the utilization side into the pump 51, and the heat medium on the utilization side precipitates substances generated by decomposition, modification, or the like. , Capture in the device.
  • the decomposition product precipitation device 57 is connected at one end downstream of the confluence of the pipe connecting the first on-off valve 54a for cooling and the pump 51 and the pipe on which the first on-off valve 55a for heating is arranged. The other end is connected to the pump 51.
  • the intermediate heat exchanger outlet temperature sensor 92 is a detection device that detects the temperature of the heat medium on the utilization side on the heat medium outflow side of the intermediate heat exchanger 5.
  • the intermediate heat exchanger outlet temperature sensor 92 is located on the pipe connecting the intermediate heat exchanger 5 and the first on-off valve 54a for cooling, rather than the confluence with the pipe on which the third on-off valve 55c for heating is arranged. It is connected upstream.
  • the user-side heat medium that circulates in the user-side cycle 120 is, for example, a refrigerant for an air conditioner such as a mixed refrigerant containing nonflammable R466A, R13I1 and R13I1.
  • the user-side heat medium mainly carries the heat exchanged between the indoor air and the user-side heat medium.
  • FIG. 7 is a diagram for explaining the flow of the heat medium during the cooling operation and the heating operation of the air conditioner according to the third embodiment.
  • the solid line and the broken line in FIG. 7 show the flow of the heat medium during the cooling operation and the heating operation, respectively.
  • the flow of the heat medium as well as the operation of each device will be described.
  • the flow of the heat source side heat medium and the operation of the equipment in the heat source side cycle 110 in the cooling operation and the heating operation are the same as those described in the first embodiment.
  • the pump 51 boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature flows into the utilization-side heat exchanger 52 via the second on-off valve 54b for cooling and the forward pipe 81a.
  • the user-side heat exchanger 52 heats a liquid user-side heat medium having an intermediate temperature and vaporizes it by evaporating it by exchanging heat with the indoor air supplied from the user-side fan 60.
  • the gas-like heat medium of intermediate temperature vaporized by the heat exchanger 52 on the user side flows into the intermediate heat exchanger 5 via the pressure reducing device 53, the return pipe 81b, and the third on-off valve 54c for cooling. ..
  • the intermediate heat exchanger 5 exchanges heat between a gaseous heat medium on the utilization side at an intermediate temperature and a heat medium on the heat source side that circulates in the heat source side cycle 110.
  • the gas-like heat medium on the utilization side at an intermediate temperature is cooled and condensed.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure condensed by the intermediate heat exchanger 5 is sucked into the pump 51 again via the first on-off valve 54a for cooling and the decomposition product precipitation device 57.
  • the intermediate heat exchanger outlet temperature sensor 92 detects the temperature of the liquid utilization side heat medium of the intermediate temperature and pressure flowing out from the intermediate heat exchanger 5. Based on the temperature detected by the intermediate heat exchanger outlet temperature sensor 92, the control device 91 relates to the device in the air conditioner 100 so that the heat medium on the user side in the cycle 120 on the user side does not exceed a predetermined set temperature. Take control.
  • the control device 91 is controlled in the utilization side cycle 120 at a temperature or lower at which the refrigerant can suppress reactions such as autolysis and alteration in the mixed refrigerant containing R466A, R13I1 and R13I1.
  • the set temperature at which the refrigerant reaction can be suppressed is preferably 100 ° C. or lower.
  • the pump 51 boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure flows into the intermediate heat exchanger 5 via the second on-off valve 55b for heating.
  • the intermediate heat exchanger 5 exchanges heat between a liquid utilization-side heat medium having an intermediate temperature and a heat source-side heat medium that circulates in the heat source-side cycle 110.
  • the liquid utilization side heat medium at intermediate temperature is heated and evaporates and vaporizes.
  • the gas-like heat medium on the utilization side having an intermediate temperature and vaporization vaporized by the intermediate heat exchanger 5 flows into the heat exchanger 52 on the utilization side via the third on-off valve 55c for heating and the outgoing pipe 81a.
  • the user-side heat exchanger 52 cools the gas-like user-side heat medium at an intermediate temperature and turns it into a condenser by heat exchange with the indoor air supplied from the user-side fan 60.
  • the liquid utilization-side heat medium having an intermediate temperature and liquefied by the utilization-side heat exchanger 52a is sucked into the pump 51 again via the heating first on-off valve 55a and the decomposition product precipitation device 57.
  • the intermediate heat exchanger outlet temperature sensor 92 detects the temperature of the gaseous heat medium on the utilization side of the intermediate temperature and pressure flowing out from the intermediate heat exchanger 5.
  • the control device 91 controls at least one device of the compressor 1, the throttle device 4, the heat source side fan 10, the pump 51, and the user side fan 60 based on the temperature detected by the intermediate heat exchanger outlet temperature sensor 92.
  • it is desirable that the control device 91 is controlled so as to be below a temperature at which the reaction of the refrigerant in the mixed refrigerant containing R466A, R13I1 and R13I1 can be suppressed in the utilization side cycle 120.
  • FIG. 8 is a diagram for explaining the flow of the heat medium on the utilization side and the state of the heat medium on the utilization side in the decomposition product precipitation apparatus during the cooling operation and the heating operation of the air conditioner according to the third embodiment.
  • the solid line and the broken line in FIG. 8 show the flow of the heat medium during the cooling operation and the heating operation, respectively.
  • the white outline and the colored coating in the receiver 56 of FIG. 8 indicate a gaseous heat medium for use and a liquid heat medium for use side, respectively.
  • the operation of the decomposition product precipitation device 57 when a two-phase heat medium on the utilization side of gas and liquid flows in will be described.
  • the flow rate of the two-phase heat medium on the utilization side that has flowed into the decomposition product precipitation device 57 from the inlet is reduced in the container of the decomposition product precipitation device 57.
  • the low-density gaseous heat medium for use moves to the upper part, and the high-density liquid heat medium for use side moves to the lower part, so that the heat medium for use side is separated in the container. Only the separated liquid utilization-side heat medium passes through the outlet pipe having an inflow port near the bottom surface of the decomposition product precipitation device 57, and the liquid utilization-side heat medium flows out from the outlet pipe.
  • the decomposition product 59 contained in the two-phase heat medium on the utilization side flowing in from the inlet is separated into the lower part of the decomposition product precipitation device 57 together with the liquid heat medium on the utilization side.
  • the cooling device 58 installed on the bottom surface of the decomposition product precipitation device 57 cools the partially liquid utilization-side heat medium.
  • the decomposition product 59 contained in the liquid utilization-side heat medium is precipitated from the cooled liquid utilization-side heat medium.
  • the precipitated decomposition product 59 is captured in the decomposition product precipitation device 57 and accumulated on the bottom surface. Therefore, it is possible to prevent the decomposition product 59 from circulating in the user-side cycle 120.
  • the cooling device 58 equipment such as a Perche type cooler can be used.
  • the piping between the heat source side flow path switching device 2 and the suction side of the compressor 1 is used as the cooling device 58, and the liquid is used by utilizing the low temperature heat generated by the heat source side heat medium.
  • the side heat medium may be cooled.
  • an example in which a two-phase heat medium for use side has flowed into the decomposition product precipitation apparatus 57 has been described, but the present invention is not limited to the two-phase heat medium for use side, and is not limited to the two-phase heat medium for use side.
  • the heat medium may flow into the decomposition product precipitation apparatus 57.
  • the decomposition product precipitation device 57 is installed in the utilization side cycle 120 to separate the gaseous utilization side heat medium and the liquid utilization side heat medium, and the liquid utilization side heat.
  • the medium was allowed to pass through. Therefore, as compared with the first embodiment, the pump 51 can be configured so that the gaseous heat medium on the utilization side does not flow into the pump 51. Therefore, the failure of the pump 51 can be avoided.
  • the decomposition product precipitation device 57 captures the decomposition product 59 in the liquid utilization-side heat medium and stores it inside, the decomposition product 59 is prevented from circulating in the utilization-side cycle 120. To do. Therefore, it is possible to avoid a failure of the air conditioner 100 due to corrosion caused by the decomposition product 59, blockage of the flow path, and the like.
  • the intermediate heat exchanger outlet temperature sensor 92 that detects the temperature of the utilization side heat medium flowing out from the intermediate heat exchanger 5 is installed in the utilization side cycle 120. Then, the control device 91 controls the device of the user-side cycle 120 based on the temperature detected by the intermediate heat exchanger outlet temperature sensor 92. Therefore, it is possible to prevent the heat medium on the user side from causing a chemical reaction or the like to be decomposed by heat, and to extend the life of the air conditioner as a whole. In addition, failure of the air conditioner 100 due to corrosion caused by the decomposition product 59 and blockage of the flow path can be avoided.
  • FIG. 9 is a diagram schematically showing an example of the configuration of the air conditioner according to the fourth embodiment.
  • devices and the like having the same configuration as the air conditioner 100 of FIG. 1 are designated by the same reference numerals.
  • the air conditioner 100 of FIG. 9 has a different configuration of the outdoor unit 101.
  • the outdoor unit 101 of the fourth embodiment is equipped with a cooling pump 51a and a heating pump 51b as elements of the user-side cycle 120.
  • the first on-off valve 54a for cooling, the second on-off valve 54b for cooling, the third on-off valve 54c for cooling, the first on-off valve 55a for heating, and the heating are mounted on the air conditioner 100 of the first embodiment.
  • the second on-off valve 55b for heating and the third on-off valve 55c for heating are not installed.
  • the cooling pump 51a and the heating pump 51b are devices that suck in a liquid heat medium on the user side and send it out in a stepped-up state.
  • the cooling pump 51a and the heating pump 51b are, for example, a turbo type non-volumetric pump.
  • FIG. 10 is a diagram for explaining the flow of the heat medium during the cooling operation and the heating operation of the air conditioner according to the fourth embodiment.
  • the solid line and the broken line in FIG. 10 show the flow of the heat medium during the cooling operation and the heating operation, respectively.
  • the flow of the heat medium as well as the operation of each device will be described.
  • the flow of the heat source side heat medium and the operation of the equipment in the heat source side cycle 110 in the cooling operation and the heating operation are the same as those described in the first embodiment.
  • the flow of the heat medium on the user side during the cooling operation will be explained.
  • the heating pump 51b is stopped.
  • the cooling pump 51a pressurizes the sucked intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure flows into the utilization-side heat exchanger 52 via the outgoing pipe 81a.
  • the user-side heat exchanger 52 heats a liquid user-side heat medium having an intermediate temperature and vaporizes it by evaporating it by exchanging heat with the indoor air supplied from the user-side fan 60.
  • the gas-like heat medium of the intermediate temperature vaporized by the heat exchanger 52 on the utilization side flows into the intermediate heat exchanger 5 via the decompression device 53, the return pipe 81b, and the stopped heating pump 51b.
  • the intermediate heat exchanger 5 exchanges heat between a gaseous heat medium on the utilization side at an intermediate temperature and a heat medium on the heat source side that circulates in the heat source side cycle 110.
  • the gas-like heat medium on the utilization side at an intermediate temperature is cooled and condensed.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure condensed by the intermediate heat exchanger 5 is sucked into the cooling pump 51a again.
  • the cooling pump 51a boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure flows into the intermediate heat exchanger 5.
  • the intermediate heat exchanger 5 exchanges heat between a liquid utilization-side heat medium having an intermediate temperature and a heat source-side heat medium that circulates in the heat source-side cycle 110.
  • the liquid utilization side heat medium at intermediate temperature is heated and evaporates and vaporizes.
  • the gas-like heat medium on the utilization side having an intermediate temperature and vaporization vaporized by the intermediate heat exchanger 5 flows into the heat exchanger 52 on the utilization side via the stopped cooling pump 51a and the forward pipe 81a.
  • the user-side heat exchanger 52 cools the gas-like user-side heat medium at an intermediate temperature and turns it into a condenser by heat exchange with the indoor air supplied from the user-side fan 60.
  • the liquid utilization-side heat medium having an intermediate temperature and liquefied by the utilization-side heat exchanger 52a is sucked into the heating pump 51b again via the decompression device 53 and the return pipe 81b.
  • the cooling pump 51a and the heating pump 51b are installed in the user-side cycle 120. Therefore, the cooling operation and the heating operation can be switched according to the operation request from the indoor unit 102. Further, the air conditioner 100 of the fourth embodiment allows the liquid utilization side heat medium to pass through the driving cooling pump 51a and the heating pump 51b so as to pass the gaseous utilization side heat medium. I tried to suppress. Therefore, it is possible to avoid a failure of the cooling pump 51a and the heating pump 51b.
  • FIG. 11 is a diagram schematically showing an example of the configuration of the air conditioner according to the fifth embodiment.
  • the same reference numerals are given to devices and the like having the same configuration as the air conditioner 100 of FIG.
  • the air conditioner 100 of FIG. 11 has a different configuration of the outdoor unit 101.
  • the outdoor unit 101 of the fifth embodiment is equipped with a reversing pump 51c as an element of the user-side cycle 120 instead of the cooling pump 51a and the heating pump 51b of the outdoor unit 101 of the fourth embodiment.
  • the reversing pump 51c is a device capable of reversing the suction side and the discharge side of the fluid. Therefore, the reversing pump 51c of the fifth embodiment can suck in the liquid heat medium on the utilization side in both the cooling operation and the heating operation, and send it out in a stepped-up state.
  • the reversing pump 51c is, for example, an inverter type centrifugal pump or a turbo type non-volumetric pump.
  • FIG. 12 is a diagram illustrating the flow of the heat medium during the cooling operation and the heating operation of the air conditioner according to the fifth embodiment.
  • the solid line and the broken line in FIG. 12 show the flow of the heat medium during the cooling operation and the heating operation, respectively.
  • the flow of the heat medium as well as the operation of each device will be described.
  • the flow of the heat source side heat medium and the operation of the equipment in the heat source side cycle 110 in the cooling operation and the heating operation are the same as those described in the first embodiment.
  • the reversing pump 51c boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure flows into the utilization-side heat exchanger 52 via the outgoing pipe 81a.
  • the user-side heat exchanger 52 heats a liquid user-side heat medium having an intermediate temperature and vaporizes it by evaporating it by exchanging heat with the indoor air supplied from the user-side fan 60.
  • the gas-like heat medium of the intermediate temperature vaporized by the heat exchanger 52 on the utilization side flows into the intermediate heat exchanger 5 via the decompression device 53 and the return pipe 81b.
  • the intermediate heat exchanger 5 exchanges heat between a gaseous heat medium on the utilization side at an intermediate temperature and a heat medium on the heat source side that circulates in the heat source side cycle 110.
  • the gas-like heat medium on the utilization side at an intermediate temperature is cooled and condensed.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure condensed by the intermediate heat exchanger 5 is sucked into the reversing pump 51c again.
  • the reversing pump 51c boosts the suctioned intermediate temperature liquid liquid utilization side heat medium.
  • the liquid utilization-side heat medium having an intermediate temperature and pressure flows into the intermediate heat exchanger 5.
  • the intermediate heat exchanger 5 exchanges heat between a liquid utilization-side heat medium having an intermediate temperature and a heat source-side heat medium that circulates in the heat source-side cycle 110.
  • the liquid utilization side heat medium at intermediate temperature is heated and evaporates and vaporizes.
  • the gas-like heat medium on the utilization side having an intermediate temperature and vaporization vaporized by the intermediate heat exchanger 5 flows into the heat exchanger 52 on the utilization side via the forward pipe 81a and the decompression device 53.
  • the user-side heat exchanger 52 cools the gas-like user-side heat medium at an intermediate temperature and turns it into a condenser by heat exchange with the indoor air supplied from the user-side fan 60.
  • the liquid utilization-side heat medium having an intermediate temperature and liquefied by the utilization-side heat exchanger 52a is sucked into the reversing pump 51c again via the return pipe 81b.
  • the reversing pump 51c is installed in the utilization side cycle 120. Therefore, the reversing pump 51c can switch between the cooling operation and the heating operation in response to the operation request from the indoor unit 102. At this time, in the air conditioner 100 of the fifth embodiment, the reversing pump 51c is allowed to pass the liquid heat medium on the utilization side. Therefore, it is possible to avoid a failure of the reversing pump 51c. Further, in the air conditioner 100 of the fifth embodiment, the phase state of the heat medium on the utilization side passing through the forward pipe 81a and the return pipe 81b can be made the same in both the cooling operation and the heating operation. Therefore, the diameter of the pipe can be reduced.
  • Embodiment 6 the air conditioner 100 of the first to fifth embodiments circulates the heat source side heat medium in the heat source side cycle 110, and in the intermediate heat exchanger 5, the heat exchange of the user side heat medium causes the user side to circulate.
  • the heat medium is made to absorb and dissipate heat.
  • the heat medium on the user side may be heated and cooled by the heating device and the cooling device.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)
PCT/JP2020/000296 2020-01-08 2020-01-08 空気調和装置 Ceased WO2021140589A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US17/775,313 US12061019B2 (en) 2020-01-08 2020-01-08 Air-conditioning apparatus
PCT/JP2020/000296 WO2021140589A1 (ja) 2020-01-08 2020-01-08 空気調和装置
JP2021569647A JP7301166B2 (ja) 2020-01-08 2020-01-08 空気調和装置
EP20911699.5A EP4089336A4 (en) 2020-01-08 2020-01-08 AIR CONDITIONING DEVICE

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Application Number Priority Date Filing Date Title
PCT/JP2020/000296 WO2021140589A1 (ja) 2020-01-08 2020-01-08 空気調和装置

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WO2021140589A1 true WO2021140589A1 (ja) 2021-07-15

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JP2024536336A (ja) * 2021-09-30 2024-10-04 エクールテック・グロスコフ・ゲーエムベーハー 温度制御される空間を温度制御するための方法および装置
EP4545875A4 (en) * 2022-06-23 2025-09-24 Panasonic Ip Man Co Ltd FREEZING APPLIANCE

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WO2022259354A1 (ja) * 2021-06-08 2022-12-15 三菱電機株式会社 冷凍サイクル装置
FR3153139B1 (fr) * 2023-09-15 2026-03-06 Valeo Systemes Thermiques Système de conditionnement thermique
DE102024205137A1 (de) * 2024-06-04 2025-12-04 ECOOLTEC Grosskopf GmbH Temperierungsanlage mit einem Sammler und einer Pumpe in dem Sekundärkreis, Verfahren zum Betreiben einer Temperierungsanlage oder Verfahren zum Herstellen einer Temperierungsanlage

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JP2024536336A (ja) * 2021-09-30 2024-10-04 エクールテック・グロスコフ・ゲーエムベーハー 温度制御される空間を温度制御するための方法および装置
EP4545875A4 (en) * 2022-06-23 2025-09-24 Panasonic Ip Man Co Ltd FREEZING APPLIANCE

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JP7301166B2 (ja) 2023-06-30
US20220373233A1 (en) 2022-11-24
JPWO2021140589A1 (https=) 2021-07-15
US12061019B2 (en) 2024-08-13
EP4089336A4 (en) 2022-12-28

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