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WO2023139700A1 - Dispositif de réfrigération et de climatisation - Google Patents

Dispositif de réfrigération et de climatisation Download PDF

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Publication number
WO2023139700A1
WO2023139700A1 PCT/JP2022/001823 JP2022001823W WO2023139700A1 WO 2023139700 A1 WO2023139700 A1 WO 2023139700A1 JP 2022001823 W JP2022001823 W JP 2022001823W WO 2023139700 A1 WO2023139700 A1 WO 2023139700A1
Authority
WO
WIPO (PCT)
Prior art keywords
indoor
refrigerant
unit
degree
pressure
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/JP2022/001823
Other languages
English (en)
Japanese (ja)
Inventor
翔太 雲川
博幸 岡野
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 EP22921859.9A priority Critical patent/EP4467897A4/fr
Priority to US18/709,579 priority patent/US20250003646A1/en
Priority to JP2023574952A priority patent/JPWO2023139700A1/ja
Priority to PCT/JP2022/001823 priority patent/WO2023139700A1/fr
Publication of WO2023139700A1 publication Critical patent/WO2023139700A1/fr
Anticipated expiration legal-status Critical
Priority to JP2025083210A priority patent/JP2025114842A/ja
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/40—Pressure, e.g. wind pressure
    • 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
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • 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
    • F25B2313/0291—Control issues related to the pressure of the indoor unit
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

  • the present disclosure relates to a refrigerating and air-conditioning apparatus capable of simultaneously performing cooling operation and heating operation for a plurality of air-conditioned spaces.
  • Patent Document 1 discloses an air conditioner that includes a plurality of indoor units, an outdoor unit that circulates a refrigerant in each indoor unit, and a control panel that controls the operation of these units, and that is configured to blow out temperature-controlled air from each indoor unit.
  • the present disclosure has been made in view of the problems in the conventional technology described above, and an object thereof is to provide a refrigerating and air-conditioning apparatus capable of individually controlling each indoor unit even when a plurality of indoor units are provided.
  • a refrigerating and air-conditioning apparatus includes an outdoor unit having a compressor and an outdoor heat exchanger, a plurality of indoor units each having an indoor expansion valve and an indoor heat exchanger, and is connected between the outdoor unit and the indoor unit, and has a plurality of three-way valves that are provided in a plurality corresponding to the number of the indoor units that switch the flow of refrigerant and adjust the flow rate of the refrigerant that passes through.
  • a relay unit for distributing a refrigerant and a control device for controlling switching and opening of the three-way valve are provided.
  • the indoor unit has an indoor pressure sensor that detects the pressure of the refrigerant passing through the indoor heat exchanger.
  • the degree of opening of the corresponding three-way valve is controlled based on the indoor pressure of the indoor unit that is performing cooling operation, so even if multiple indoor units are provided, each indoor unit can be controlled individually.
  • FIG. 1 is a circuit diagram showing an example of a configuration of a refrigerating and air-conditioning apparatus according to Embodiment 1;
  • FIG. FIG. 2 is a functional block diagram showing an example of the configuration of a control device in FIG. 1;
  • FIG. FIG. 3 is a hardware configuration diagram showing an example of the configuration of a control device in FIG. 2;
  • 3 is a hardware configuration diagram showing another example of the configuration of the control device in FIG. 2;
  • FIG. FIG. 2 is a schematic diagram for explaining the flow of refrigerant in a cooling only operation mode in the refrigerating and air-conditioning apparatus of FIG. 1;
  • FIG. 2 is a schematic diagram for explaining the flow of refrigerant in a heating only operation mode in the refrigerating and air-conditioning apparatus of FIG.
  • FIG. 2 is a schematic diagram for explaining the flow of refrigerant in a cooling-main operation mode in the refrigerating and air-conditioning apparatus of FIG. 1;
  • FIG. 2 is a schematic diagram for explaining the flow of refrigerant in a heating-main operation mode in the refrigerating and air-conditioning apparatus of FIG. 1;
  • 4 is a flowchart showing an example of the flow of evaporation temperature adjustment processing according to Embodiment 1;
  • 5 is a flowchart showing an example of the flow of liquid backflow suppression processing according to Embodiment 1;
  • FIG. 11 is a flow chart showing an example of the flow of the first liquid bagging suppression process of FIG. 10;
  • FIG. FIG. 11 is a flow chart showing an example of the flow of the second liquid bagging suppression process of FIG. 10;
  • FIG. FIG. 7 is a circuit diagram showing an example of the configuration of a refrigerating and air-conditioning apparatus according to Embodiment 2;
  • Embodiment 1 A refrigerating and air-conditioning apparatus according to Embodiment 1 will be described.
  • the refrigerating and air-conditioning apparatus according to Embodiment 1 performs only cooling operation, only heating operation, or simultaneous cooling and heating operation for a plurality of air-conditioned spaces.
  • FIG. 1 is a circuit diagram showing an example of the configuration of a refrigerating and air-conditioning apparatus according to Embodiment 1.
  • FIG. A refrigerating and air-conditioning apparatus 100 according to Embodiment 1 includes an outdoor unit 10 , a plurality of indoor units 20 , a relay unit 30 and a control device 40 .
  • the refrigerating and air-conditioning apparatus 100 is composed of one outdoor unit 10, five indoor units 20a to 20e, and one relay unit 30.
  • FIG. 1 is a circuit diagram showing an example of the configuration of a refrigerating and air-conditioning apparatus according to Embodiment 1.
  • FIG. A refrigerating and air-conditioning apparatus 100 according to Embodiment 1 includes an outdoor unit 10 , a plurality of indoor units 20 , a relay unit 30 and a control device 40 .
  • the refrigerating and air-conditioning apparatus 100 is composed of one outdoor unit 10, five indoor units 20a to 20e, and one relay unit 30.
  • a refrigerant circuit is formed by connecting the outdoor unit 10, the relay unit 30 and the indoor units 20a to 20e with a high pressure pipe 101 and a low pressure pipe .
  • the number of indoor units 20 is not limited to this example, and may be two or more and four or less, or may be six or more.
  • the indoor units 20a to 20e are installed in rooms 1a to 1e, which are different spaces to be air-conditioned.
  • the outdoor unit 10 and the relay unit 30, and the indoor units 20a to 20e and the relay unit 30 are connected by high pressure pipes 101 and low pressure pipes 102, respectively.
  • FIG. 1 omits the configuration connected to the indoor units 20c and 20d among the circuit configurations of the indoor units 20c and 20d and the relay unit 30. Also, since the circuit configurations of the indoor units 20b and 20e are the same as those of the indoor unit 20a, illustration thereof is omitted.
  • the outdoor unit 10 includes a compressor 11, a refrigerant flow switching device 12, an outdoor heat exchanger 13, an outdoor expansion valve 14, check valves 15a to 15d and an accumulator 16.
  • the outdoor unit 10 also includes an outdoor pressure sensor 17 and an outdoor temperature sensor 18 .
  • the compressor 11 sucks in a low-temperature, low-pressure refrigerant, compresses the refrigerant into a high-temperature, high-pressure state, and discharges it.
  • the compressor 11 for example, an inverter compressor or the like is used, which can control the capacity, which is the amount of refrigerant delivered per unit time, by arbitrarily changing the drive frequency.
  • the driving frequency of the compressor 11 is controlled by a control device 40 which will be described later.
  • the refrigerant flow switching device 12 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction of refrigerant flow. Switching of the refrigerant flow switching device 12 is controlled by the control device 40 . Note that the refrigerant flow switching device 12 is not limited to this example, and may be configured by combining other valves such as a two-way valve or a three-way valve.
  • the outdoor heat exchanger 13 exchanges heat between air supplied by a blower such as a fan (not shown) (hereinafter referred to as "outdoor air” as appropriate) and the refrigerant.
  • the outdoor heat exchanger 13 functions as a condenser that radiates the heat of the refrigerant to the outdoor air to condense the refrigerant during the cooling operation.
  • the outdoor heat exchanger 13 functions as an evaporator that evaporates the refrigerant and absorbs heat from the outdoor air as heat of vaporization during the heating operation.
  • the outdoor expansion valve 14 decompresses and expands the refrigerant by adjusting the flow rate of the refrigerant.
  • the outdoor expansion valve 14 is configured by, for example, a valve such as an electronic expansion valve whose degree of opening can be controlled. In this case, the degree of opening of the outdoor expansion valve 14 is controlled by the controller 40 . Note that the outdoor expansion valve 14 is not limited to this example, and other expansion devices such as capillaries may be used.
  • the check valves 15a to 15d allow the refrigerant to flow through the refrigerant circuit only in a predetermined direction.
  • the check valve 15 a is provided in the high pressure pipe 101 between the outdoor heat exchanger 13 and the relay unit 30 .
  • the check valve 15a allows the refrigerant to flow only in the direction from the outdoor unit 10 to the relay unit 30 during the cooling operation including the cooling only operation and the cooling main operation, which will be described later.
  • the check valve 15 d is provided in the low-pressure pipe 102 between the relay unit 30 and the refrigerant flow switching device 12 .
  • the check valve 15d allows the refrigerant to flow only in the direction from the relay unit 30 to the outdoor unit 10 during cooling operation.
  • the check valve 15b is provided in the first connection pipe 103 that connects the high-pressure pipe 101 downstream of the check valve 15a and the low-pressure pipe 102 downstream of the check valve 15d.
  • the check valve 15b allows the refrigerant to flow only in the direction from the compressor 11 to the relay unit 30 during the heating operation including the heating only operation and the heating main operation, which will be described later.
  • the check valve 15c is provided in a second connection pipe 104 that connects the upstream side of the check valve 15a in the high pressure pipe 101 and the upstream side of the check valve 15d in the low pressure pipe 102 .
  • the check valve 15c allows the refrigerant to flow only in the direction from the relay unit 30 to the compressor 11 during heating operation.
  • the accumulator 16 is provided on the low pressure side, which is the suction side of the compressor 11 .
  • the accumulator 16 stores surplus refrigerant caused by the difference in operating conditions between cooling operation and heating operation, surplus refrigerant due to transient changes in operation, and the like. Note that the accumulator 16 may not necessarily be provided.
  • the outdoor pressure sensor 17 is provided in the pipe between the refrigerant suction side of the compressor 11 and the refrigerant flow switching device 12 .
  • the outdoor pressure sensor 17 detects suction pressure, which is the pressure of the refrigerant sucked into the compressor 11 .
  • the outdoor temperature sensor 18 is provided in a pipe between the refrigerant suction side of the compressor 11 and the refrigerant flow switching device 12 .
  • the outdoor temperature sensor 18 detects the suction temperature, which is the temperature of the refrigerant sucked into the compressor 11 .
  • the indoor units 20a to 20e respectively cool and heat the air in the rooms 1a to 1e, for example.
  • Each of the indoor units 20a-20e includes an indoor expansion valve 21 and an indoor heat exchanger 22.
  • the indoor units 20a to 20e each have an indoor pressure sensor 23.
  • the indoor units 20a to 20e need not be distinguished from each other, they will be simply referred to as "indoor unit 20".
  • the indoor expansion valve 21 decompresses and expands the refrigerant by adjusting the flow rate of the refrigerant.
  • the indoor expansion valve 21 is configured by, for example, a valve such as an electronic expansion valve whose opening degree can be controlled. In this case, the degree of opening of the indoor expansion valve 21 is controlled by the controller 40 . Note that the indoor expansion valve 21 is not limited to this example, and other throttle devices such as a capillary may be used.
  • the indoor heat exchanger 22 exchanges heat between air supplied by a blower such as a fan (not shown) and the refrigerant. As a result, heating air or cooling air to be supplied to the rooms 1a to 1e is generated. Specifically, the indoor heat exchanger 22 functions as an evaporator during the cooling operation, and cools the air in the rooms 1a to 1e, which are the spaces to be air-conditioned. Further, the indoor heat exchanger 22 functions as a condenser during the heating operation, and heats the air in the rooms 1a to 1e for heating.
  • the indoor pressure sensor 23 is provided in the low-pressure pipe 102 between the indoor heat exchanger 22 and the relay unit 30.
  • the indoor pressure sensor 23 detects the indoor pressure, which is the pressure of the refrigerant passing through the indoor heat exchanger 22 .
  • the indoor pressure sensor 23 detects a pressure equivalent to the evaporating pressure in the indoor heat exchanger 22 .
  • the indoor pressure at this time is detected, for example, by inserting a sensor into the pipe or by determining the relationship between the amount of deformation of the pipe detected by a strain sensor attached to the pipe and the pressure applied to the pipe.
  • the relay unit 30 switches the flow of the refrigerant according to the operating conditions of the indoor units 20 so that the low-temperature refrigerant is distributed to the indoor units 20 that perform the cooling operation and the high-temperature refrigerant is distributed to the indoor units 20 that perform the heating operation.
  • the relay unit 30 includes a gas-liquid separator 31 , a first refrigerant heat exchanger 32 , a first relay expansion valve 33 , a second refrigerant heat exchanger 34 , a second relay expansion valve 35 , a check valve 36 and a three-way linear expansion valve 37 . Further, the relay unit 30 is provided with a gas pipe 105 through which gas refrigerant flows and a liquid pipe 106 through which liquid refrigerant flows. Further, the relay unit 30 is provided with a branch pipe 107 and a confluence pipe 108 .
  • the branch pipe 107 is a pipe branched from the downstream side of the second refrigerant heat exchanger 34 in the liquid pipe 106 and connected to the low-pressure pipe 102 .
  • the confluence pipe 108 is a pipe that is connected to each indoor unit 20 and merges with the liquid pipe 106 between the first relay expansion valve 33 and the second refrigerant heat exchanger 34 .
  • the gas-liquid separator 31 is connected to the high-pressure pipe 101, the gas pipe 105 and the liquid pipe 106, and separates the two-phase refrigerant flowing through the high-pressure pipe 101 into gas refrigerant and liquid refrigerant.
  • the gas refrigerant separated by the gas-liquid separator 31 is supplied to the three-way linear expansion valve 37 via the gas pipe 105 .
  • the liquid refrigerant separated by the gas-liquid separator 31 is supplied to the first refrigerant heat exchanger 32 via the liquid pipe 106 .
  • the first refrigerant heat exchanger 32 has a primary side channel and a secondary side channel, performs heat exchange between the refrigerant flowing in the primary side channel and the refrigerant flowing in the secondary side channel, and supercools the refrigerant flowing in the primary side channel.
  • the primary side flow path of the first refrigerant heat exchanger 32 is connected to the gas-liquid separator 31 and the first relay expansion valve 33, and the liquid refrigerant separated by the gas-liquid separator 31 flows.
  • the secondary flow path of the second refrigerant heat exchanger 34 and the low-pressure pipe 102 are connected to the secondary flow path of the first refrigerant heat exchanger 32, and the refrigerant flowing out of the secondary flow path of the second refrigerant heat exchanger 34 flows.
  • the first relay expansion valve 33 is connected to the primary side passage of the first refrigerant heat exchanger 32 and the primary side passage of the second refrigerant heat exchanger 34 .
  • the first relay expansion valve 33 decompresses and expands the refrigerant by adjusting the flow rate of the refrigerant.
  • the first relay expansion valve 33 is configured by, for example, a valve such as an electronic expansion valve whose degree of opening can be controlled. In this case, the opening degree of the first relay expansion valve 33 is controlled by the controller 40 . It should be noted that the first relay expansion valve 33 is not limited to this example, and other expansion devices such as capillaries may be used.
  • the second refrigerant heat exchanger 34 has a primary side passage and a secondary side passage, performs heat exchange between the refrigerant flowing in the primary side passage and the refrigerant flowing in the secondary side passage, and supercools the refrigerant flowing in the primary side passage.
  • the first relay expansion valve 33 is connected to the primary side passage of the second refrigerant heat exchanger 34, and the refrigerant flowing out from the first relay expansion valve 33 flows.
  • the secondary flow path of the second refrigerant heat exchanger 34 is connected to the secondary flow paths of the second relay expansion valve 35 and the first refrigerant heat exchanger 32, and the refrigerant flowing out of the second relay expansion valve 35 flows.
  • the second relay expansion valve 35 is provided in the branch pipe 107 and connected to the secondary flow path of the second refrigerant heat exchanger 34 on the downstream side.
  • the second relay expansion valve 35 decompresses and expands the refrigerant by adjusting the flow rate of the refrigerant.
  • the second relay expansion valve 35 is configured by, for example, a valve whose opening degree can be controlled, such as an electronic expansion valve. In this case, the degree of opening of the second relay expansion valve 35 is controlled by the controller 40 .
  • the second relay expansion valve 35 is not limited to this example, and other expansion devices such as a capillary may be used.
  • the check valve 36 allows the refrigerant to flow through the refrigerant circuit only in a predetermined direction.
  • the check valves 36 are provided according to the number of the indoor units 20 . Specifically, in the example of FIG. 1, check valves 36a1 and 36a2 are provided to correspond to the indoor unit 20a, and check valves 36b1 and 36b2 are provided to correspond to the indoor unit 20b. Check valves 36c1 and 36c2 are provided to correspond to the indoor unit 20c, and check valves 36d1 and 36d2 are provided to correspond to the indoor unit 20d. Furthermore, check valves 36e1 and 36e2 are provided to correspond to the indoor unit 20e.
  • the check valves 36a1, 36b1, 36c1, 36d1 and 36e1 are provided between the indoor units 20a to 20e and the confluence pipe 108, respectively.
  • the check valves 36a1, 36b1, 36c1, 36d1, and 36e1 allow the refrigerant to flow from the indoor units 20a to 20e toward the junction pipe .
  • the check valves 36a2, 36b2, 36c2, 36d2 and 36e2 are respectively provided between the downstream side of the primary side passage of the second refrigerant heat exchanger 34 and the indoor units 20a to 20e.
  • the check valves 36a2, 36b2, 36c2, 36d2 and 36e2 allow refrigerant to flow from the second refrigerant heat exchanger 34 toward the indoor units 20a-20e.
  • the three-way linear expansion valve 37 is connected to the indoor unit 20, the low-pressure pipe 102 and the gas pipe 105, and switches the direction of refrigerant flow according to the operating conditions of the indoor unit 20. Specifically, the three-way linear expansion valve 37 switches connection so that the indoor unit 20 and the low-pressure pipe 102 communicate with each other when the indoor unit 20 performs cooling operation. In addition, the three-way linear expansion valve 37 switches connection so that the gas pipe 105 and the indoor unit 20 communicate with each other when the indoor unit 20 performs the heating operation.
  • the three-way linear expansion valve 37 also has a function of decompressing and expanding the refrigerant by adjusting the flow rate of the refrigerant.
  • the three-way linear expansion valve 37 is composed of, for example, an electronic expansion valve whose degree of opening can be controlled. Switching and opening of the three-way linear expansion valve 37 are controlled by the controller 40 .
  • the three-way linear expansion valves 37 are provided according to the number of indoor units 20 . Specifically, in the example of FIG. 1, three-way linear expansion valves 37a-37e are provided corresponding to the indoor units 20a-20e, respectively.
  • control device 40 The control device 40 controls the entire refrigerating and air-conditioning device 100 .
  • the control device 40 controls the refrigerant flow switching device 12, the outdoor expansion valve 14, the indoor expansion valve 21, the first relay expansion valve 33, the second relay expansion valve 35, the three-way linear expansion valve 37, and the like, depending on the operating conditions of the refrigerating and air-conditioning device 100.
  • the control device 40 controls the opening degree of the three-way linear expansion valve 37 to individually adjust the evaporation temperature of the indoor heat exchangers 22 provided in the respective indoor units 20. Performs evaporation temperature adjustment processing. Further, the control device 40 performs liquid backflow suppression processing for suppressing liquid backflow to the compressor 11 . Details of these processes will be described later.
  • FIG. 2 is a functional block diagram showing an example of the configuration of the control device of FIG.
  • the control device 40 includes an information acquisition section 41 , a calculation section 42 , a comparison section 43 , a valve control section 44 and a storage section 45 .
  • the control device 40 implements various functions by executing software on an arithmetic device such as a microcomputer, or is configured with hardware such as circuit devices that implement various functions. It should be noted that, of the functions possessed by the control device 40, only the functions related to the characteristic processing in the first embodiment will be described here.
  • the information acquisition unit 41 acquires the suction pressure detected by the outdoor pressure sensor 17, the suction temperature detected by the outdoor temperature sensor 18, and the indoor pressure detected by the indoor pressure sensor 23, respectively.
  • the suction pressure is the pressure of the refrigerant sucked into the compressor 11 .
  • the suction temperature is the temperature of the refrigerant sucked into the compressor 11 .
  • the calculation unit 42 derives the saturation temperature, which is the evaporation temperature, from the pressure acquired by the information acquisition unit 41 . Specifically, during the evaporating temperature adjustment process, the computing unit 42 derives the evaporating temperature of the indoor heat exchanger 22 provided in the indoor unit 20 that is performing the cooling operation from the indoor pressure detected by the indoor pressure sensor 23 and acquired by the information acquiring unit 41. Further, the calculation unit 42 derives the evaporation temperature based on the suction pressure detected by the outdoor pressure sensor 17 and acquired by the information acquisition unit 41 during the liquid backflow suppression process. Further, the calculation unit 42 calculates the degree of superheat based on the suction temperature detected by the outdoor temperature sensor 18 and acquired by the information acquisition unit 41 and the calculated evaporation temperature during the liquid backflow suppression process.
  • the comparison unit 43 compares various values calculated by the calculation unit 42 with the setting values stored in the storage unit 45 . Specifically, the comparison unit 43 compares the evaporation temperature derived by the calculation unit 42 with the set evaporation temperature stored in the storage unit 45 during the evaporation temperature adjustment process.
  • the set evaporating temperature is the evaporating temperature that should be set when the room is cooled to the set temperature.
  • the comparison unit 43 compares the degree of superheat calculated by the calculation unit 42 with the set degree of superheat stored in the storage unit 45 during the liquid backflow suppression process.
  • the set degree of superheat is a preset value for suppressing liquid backflow, and is determined by, for example, the outside air temperature, refrigerant pressure, refrigerant temperature, etc. in the refrigerating and air-conditioning apparatus 100 .
  • the valve control unit 44 controls the valve opening degrees of the outdoor expansion valve 14 , the indoor expansion valve 21 and the three-way linear expansion valve 37 based on the comparison result by the comparison unit 43 .
  • the valve control unit 44 controls the valve opening degree of the three-way linear expansion valve 37 based on the result of comparison between the evaporation temperature and the set evaporation temperature by the comparison unit 43 during the evaporation temperature adjustment process.
  • the valve control unit 44 controls the valve opening degrees of the outdoor expansion valve 14, the indoor expansion valve 21, and the three-way linear expansion valve 37 based on the comparison result between the degree of superheat and the set degree of superheat by the comparison unit 43 during the liquid backflow suppression process.
  • the storage unit 45 stores various values used in each unit of the control device 40 .
  • the storage unit 45 preliminarily stores the set evaporation temperature used in comparison with the evaporation temperature in the comparison unit 43 and the set degree of superheat used in comparison with the degree of superheat.
  • FIG. 3 is a hardware configuration diagram showing an example of the configuration of the control device in FIG.
  • the control device 40 of FIG. 2 is configured with a processing circuit 51 as shown in FIG.
  • Each function of the information acquisition unit 41 , the calculation unit 42 , the comparison unit 43 , the valve control unit 44 and the storage unit 45 shown in FIG. 2 is realized by the processing circuit 51 .
  • the processing circuit 51 is, for example, a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination thereof.
  • the functions of the information acquisition unit 41, the calculation unit 42, the comparison unit 43, the valve control unit 44, and the storage unit 45 may be realized by the processing circuit 51, or the functions of each unit may be realized by one processing circuit 51.
  • FIG. 4 is a hardware configuration diagram showing another example of the configuration of the control device in FIG.
  • the control device 40 of FIG. 2 is composed of a processor 52 and a memory 53 as shown in FIG.
  • Each function of the information acquisition unit 41 , the calculation unit 42 , the comparison unit 43 , the valve control unit 44 and the storage unit 45 is realized by the processor 52 and the memory 53 .
  • the functions of the information acquisition unit 41, the calculation unit 42, the comparison unit 43, the valve control unit 44, and the storage unit 45 are realized by software, firmware, or a combination of software and firmware.
  • Software and firmware are written as programs and stored in the memory 53 .
  • the processor 52 realizes the function of each unit by reading and executing the programs stored in the memory 53 .
  • non-volatile or volatile semiconductor memories such as RAM (Random Access Memory), ROM (Read Only Memory), flash memory, EPROM (Erasable and Programmable ROM) and EEPROM (Electrically Erasable and Programmable ROM) are used.
  • RAM Random Access Memory
  • ROM Read Only Memory
  • flash memory EPROM (Erasable and Programmable ROM)
  • EEPROM Electrical Erasable and Programmable ROM
  • removable recording media such as a magnetic disk, a flexible disk, an optical disk, a CD (Compact Disc), an MD (Mini Disc), and a DVD (Digital Versatile Disc) may be used.
  • the refrigerating and air-conditioning apparatus 100 operates in one of the cooling-only operation, heating-only operation, cooling-main operation, and heating-main operation.
  • the cooling only operation is an operation in which all indoor units 20 perform cooling operation.
  • the heating only operation is an operation in which all the indoor units 20 perform the heating operation.
  • Cooling-dominant operation is an operation that is performed when the cooling load of the indoor unit 20 that performs cooling operation exceeds the heating load of the indoor unit 20 that performs heating operation.
  • the heating-dominant operation is an operation performed when the heating load of the indoor unit 20 performing the heating operation exceeds the cooling load of the indoor unit 20 performing the cooling operation.
  • the cooling load exceeds the heating load and the cooling-dominant operation is performed, for example, when the number of indoor units 20 performing cooling operation is greater than the number of indoor units 20 performing heating operation.
  • the heating load exceeds the cooling load and the heating main operation is performed, for example, when the number of the indoor units 20 performing the heating operation is larger than the number of the indoor units 20 performing the cooling operation.
  • FIG. 5 is a schematic diagram for explaining the flow of refrigerant in the cooling only operation mode in the refrigerating and air-conditioning apparatus of FIG. In the cooling only operation mode, all the indoor units 20a to 20e perform cooling operation.
  • the flow path indicated by the thick line is the refrigerant flow path in the cooling only operation mode, and the arrow indicates the flow direction of the refrigerant in the refrigerant flow path.
  • the refrigerant flow switching device 12 in the outdoor unit 10 is switched so that the discharge side of the compressor 11 and the outdoor heat exchanger 13 are connected, and the suction side of the compressor 11 and the low pressure pipe 102 are connected. Also, the three-way linear expansion valves 37a to 37e are switched so that the indoor unit 20 and the low-pressure pipe 102 are connected.
  • the low-temperature, low-pressure refrigerant is compressed by the compressor 11 and discharged as a high-temperature, high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 13 via the refrigerant flow switching device 12 .
  • the high-temperature, high-pressure gas refrigerant that has flowed into the outdoor heat exchanger 13 is condensed while exchanging heat with outdoor air to release heat, and flows out of the outdoor heat exchanger 13 as a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 13 flows out of the outdoor unit 10 via the check valve 15 a and flows into the relay unit 30 .
  • the high-pressure liquid refrigerant that has flowed into the relay unit 30 flows through the gas-liquid separator 31 into the primary flow path of the first refrigerant heat exchanger 32 .
  • the liquid refrigerant that has flowed into the primary flow path of the first refrigerant heat exchanger 32 is supercooled by the refrigerant flowing through the secondary flow path of the first refrigerant heat exchanger 32, and flows out of the primary flow path of the first refrigerant heat exchanger 32.
  • the liquid refrigerant that has flowed out of the primary side passage of the first refrigerant heat exchanger 32 passes through the first relay expansion valve 33 and flows into the primary side passage of the second refrigerant heat exchanger 34 .
  • the liquid refrigerant that has flowed into the primary channel of the second refrigerant heat exchanger 34 is further supercooled by the refrigerant flowing through the secondary channel of the second refrigerant heat exchanger 34, and flows out of the primary channel of the second refrigerant heat exchanger 34.
  • the liquid refrigerant that has flowed out of the primary-side channel of the second refrigerant heat exchanger 34 is split, and part of the liquid refrigerant flows out of the relay unit 30 via the check valves 36a2, 36b2, 36c2, 36d2, and 36e2. Then, the liquid refrigerant flowing out from the relay unit 30 flows into the indoor units 20a to 20e.
  • the rest of the liquid refrigerant that has flowed out of the primary flow path of the second refrigerant heat exchanger 34 is decompressed and expanded by the second relay expansion valve 35 to become low-pressure gas refrigerant and passes through the branch pipe 107 .
  • the low-pressure gas refrigerant contributes to subcooling of the refrigerant flowing through the first refrigerant heat exchanger 32 and the second refrigerant heat exchanger 34 via the gas-liquid separator 31 .
  • the liquid refrigerant that has flowed into the indoor unit 20 a is decompressed and expanded by the indoor expansion valve 21 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant or liquid refrigerant, and flows into the indoor heat exchanger 22 .
  • the low-temperature and low-pressure gas-liquid two-phase refrigerant or liquid refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the indoor air, absorbs heat, and evaporates to cool the indoor air, becoming a low-pressure gas refrigerant and flows out of the indoor heat exchanger 22. Then, the low-pressure gas refrigerant that has flowed out of the indoor heat exchanger 22 flows out of the indoor unit 20 a and flows into the relay unit 30 .
  • the liquid refrigerant that has flowed into the indoor units 20b-20e also becomes low-pressure gas refrigerant, flows out from the indoor units 20b-20e, and flows into the relay unit 30.
  • the gas refrigerant that has flowed into the relay unit 30 reaches the low-pressure pipe 102 via the three-way linear expansion valves 37a-37e.
  • the low-pressure gas refrigerant flowing through the low-pressure pipe 102 flows out from the primary flow path of the second refrigerant heat exchanger 34, passes through the second relay expansion valve 35, the second refrigerant heat exchanger 34, and the first refrigerant heat exchanger 32 and joins the refrigerant flowing through the branch pipe 107.
  • This low-pressure gas refrigerant flows out from the relay unit 30 and flows into the outdoor unit 10 .
  • the low-pressure gas refrigerant that has flowed into the outdoor unit 10 passes through the check valve 15d, the refrigerant flow switching device 12, and the accumulator 16, and is sucked into the compressor 11. Thereafter, the above-described circulation is repeated.
  • FIG. 6 is a schematic diagram for explaining the flow of refrigerant in the heating only operation mode in the refrigerating and air-conditioning apparatus of FIG.
  • the heating only operation mode all the indoor units 20a to 20e perform heating operation.
  • the flow path indicated by the thick line is the refrigerant flow path in the heating only operation mode, and the arrow indicates the flow direction of the refrigerant in the refrigerant flow path.
  • the refrigerant flow switching device 12 in the outdoor unit 10 is switched so that the discharge side of the compressor 11 and the gas-liquid separator 31 of the relay unit 30 are connected, and the suction side of the compressor 11 and the outdoor heat exchanger 13 are connected. Also, the three-way linear expansion valves 37a to 37e are switched so that the gas pipe 105 and the indoor unit 20 are connected.
  • the low-temperature, low-pressure refrigerant is compressed by the compressor 11 and discharged as a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 11 flows out of the outdoor unit 10 via the refrigerant flow switching device 12 and the check valve 15b and flows into the relay unit 30 .
  • the high-temperature, high-pressure gas refrigerant that has flowed into the relay unit 30 flows out of the relay unit 30 via the gas-liquid separator 31 and the three-way linear expansion valves 37a-37e, and flows into the indoor units 20a-20e.
  • the high-temperature, high-pressure gas refrigerant that has flowed into the indoor unit 20a flows into the indoor heat exchanger 22, heats the indoor air by condensing while exchanging heat with the indoor air, and flows out of the indoor heat exchanger 22 as a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant that has flowed out of the indoor heat exchanger 22 is decompressed and expanded by the indoor expansion valve 21 to become an intermediate-pressure liquid refrigerant.
  • the high-temperature and high-pressure gas refrigerants that have flowed into the indoor units 20b-20e also similarly become intermediate-pressure liquid refrigerants, flow out of the indoor units 20b-20e, and flow into the relay unit 30.
  • the intermediate-pressure liquid refrigerant that has flowed into the relay unit 30 flows through the junction pipe 108 via the check valves 36a1, 36b1, 36c1, 36d1, and 36e1. After that, the intermediate-pressure liquid refrigerant passes through the second refrigerant heat exchanger 34 , becomes low-pressure liquid refrigerant by the second relay expansion valve 35 , and reaches the low-pressure pipe 102 via the first refrigerant heat exchanger 32 . The low-pressure liquid refrigerant flowing through the low-pressure pipe 102 flows out from the relay unit 30 and flows into the outdoor unit 10 .
  • the low-pressure liquid refrigerant that has flowed into the outdoor unit 10 flows into the outdoor heat exchanger 13 via the check valve 15 c and the outdoor expansion valve 14 .
  • the low-pressure liquid refrigerant that has flowed into the outdoor heat exchanger 13 exchanges heat with outdoor air, absorbs heat, evaporates, and flows out of the outdoor heat exchanger 13 as a low-temperature, low-pressure gas refrigerant.
  • the low-temperature, low-pressure gas refrigerant that has flowed out of the outdoor heat exchanger 13 passes through the refrigerant flow switching device 12 and the accumulator 16 and is sucked into the compressor 11 . Thereafter, the above-described circulation is repeated.
  • FIG. 7 is a schematic diagram for explaining the flow of refrigerant in the cooling-main operation mode in the refrigerating and air-conditioning apparatus of FIG.
  • the indoor units 20a to 20d perform the cooling operation and the indoor unit 20e performs the heating operation.
  • the flow path indicated by a thick line is the refrigerant flow path in the cooling main operation mode, and the direction of flow of the refrigerant in the refrigerant flow path is indicated by arrows.
  • the refrigerant flow switching device 12 in the outdoor unit 10 is switched so that the discharge side of the compressor 11 and the outdoor heat exchanger 13 are connected, and the suction side of the compressor 11 and the low pressure pipe 102 are connected. Also, the three-way linear expansion valves 37a to 37d are switched so that the indoor unit 20 and the low-pressure pipe 102 are connected. The three-way linear expansion valve 37e is switched so that the gas pipe 105 and the indoor unit 20 are connected.
  • the low-temperature, low-pressure refrigerant is compressed by the compressor 11 and discharged as a high-temperature, high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 flows into the outdoor heat exchanger 13 via the refrigerant flow switching device 12 .
  • the high-temperature and high-pressure gas refrigerant that has flowed into the outdoor heat exchanger 13 is condensed while exchanging heat with the outdoor air and releasing heat, and flows out of the outdoor heat exchanger 13 as a high-pressure gas-liquid two-phase refrigerant.
  • the high-pressure gas-liquid two-phase refrigerant that has flowed out of the outdoor heat exchanger 13 flows out of the outdoor unit 10 via the check valve 15 a and flows into the relay unit 30 .
  • the high-pressure gas-liquid two-phase refrigerant that has flowed into the relay unit 30 flows into the gas-liquid separator 31 and is separated into a high-pressure gas refrigerant and a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant separated by the gas-liquid separator 31 flows into the primary side passage of the first refrigerant heat exchanger 32 .
  • the liquid refrigerant that has flowed into the primary flow path of the first refrigerant heat exchanger 32 is supercooled by the refrigerant flowing through the secondary flow path of the first refrigerant heat exchanger 32, and flows out of the primary flow path of the first refrigerant heat exchanger 32.
  • the liquid refrigerant that has flowed out of the primary side passage of the first refrigerant heat exchanger 32 passes through the first relay expansion valve 33 and flows into the primary side passage of the second refrigerant heat exchanger 34 .
  • the intermediate-pressure liquid refrigerant that has flowed into the primary channel of the second refrigerant heat exchanger 34 is further supercooled by the refrigerant flowing through the secondary channel of the second refrigerant heat exchanger 34, and flows out of the primary channel of the second refrigerant heat exchanger 34.
  • the liquid refrigerant that has flowed out of the primary-side channel of the second refrigerant heat exchanger 34 is split, and part of the liquid refrigerant flows out of the relay unit 30 via the check valves 36a2, 36b2, 36c2, and 36d2. Then, the liquid refrigerant flowing out from the relay unit 30 flows into the indoor units 20a to 20d.
  • the rest of the liquid refrigerant that has flowed out of the primary flow path of the second refrigerant heat exchanger 34 is decompressed and expanded by the second relay expansion valve 35 to become low-pressure gas refrigerant and passes through the branch pipe 107 .
  • the low-pressure gas refrigerant contributes to subcooling of the refrigerant flowing through the first refrigerant heat exchanger 32 and the second refrigerant heat exchanger 34 via the gas-liquid separator 31 .
  • the liquid refrigerant that has flowed into the indoor unit 20 a is decompressed and expanded by the indoor expansion valve 21 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant or liquid refrigerant, and flows into the indoor heat exchanger 22 .
  • the low-temperature and low-pressure gas-liquid two-phase refrigerant or liquid refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the indoor air, absorbs heat, and evaporates to cool the indoor air, becoming a low-pressure gas refrigerant and flows out of the indoor heat exchanger 22. Then, the low-pressure gas refrigerant that has flowed out of the indoor heat exchanger 22 flows out of the indoor unit 20 a and flows into the relay unit 30 .
  • the liquid refrigerants that have flowed into the indoor units 20b-20d also become low-pressure gas refrigerants, flow out of the indoor units 20b-20e, and flow into the relay unit 30.
  • the refrigerant that has flowed into the relay unit 30 reaches the low-pressure pipe 102 via the three-way linear expansion valves 37a-37d.
  • the high-pressure gas refrigerant separated by the gas-liquid separator 31 flows out from the relay unit 30 via the three-way linear expansion valve 37e and flows into the indoor unit 20e in heating operation.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the indoor unit 20e flows into the indoor heat exchanger 22, heats the indoor air by condensing while exchanging heat with the indoor air and releasing heat, and becomes a high-pressure liquid refrigerant and flows out of the indoor heat exchanger 22.
  • the high-pressure liquid refrigerant that has flowed out of the indoor heat exchanger 22 is decompressed and expanded by the indoor expansion valve 21 to become liquid refrigerant.
  • the refrigerant that has flowed into the relay unit 30 flows through the confluence pipe 108 via the check valve 36e1, and reaches the low-pressure pipe 102 via the second refrigerant heat exchanger 34, the second relay expansion valve 35, and the first refrigerant heat exchanger 32.
  • the refrigerants flowing out from the indoor units 20a to 20d in which the cooling operation is performed and the indoor unit 20e in which the heating operation is performed merge in the low-pressure pipe 102, flow out from the relay unit 30, and then flow into the outdoor unit 10.
  • the low-pressure gas refrigerant that has flowed into the outdoor unit 10 passes through the check valve 15 d , the refrigerant flow switching device 12 and the accumulator 16 and is sucked into the compressor 11 . Thereafter, the above-described circulation is repeated.
  • FIG. 8 is a schematic diagram for explaining the flow of refrigerant in the heating main operation mode in the refrigerating and air-conditioning apparatus of FIG.
  • the indoor units 20a to 20d perform the heating operation and the indoor unit 20e performs the cooling operation.
  • the flow path indicated by a thick line is the refrigerant flow path in the heating main operation mode, and the direction of flow of the refrigerant in the refrigerant flow path is indicated by arrows.
  • the refrigerant flow switching device 12 in the outdoor unit 10 is switched so that the discharge side of the compressor 11 and the gas-liquid separator 31 of the relay unit 30 are connected, and the suction side of the compressor 11 and the outdoor heat exchanger 13 are connected. Also, the three-way linear expansion valves 37a to 37d are switched so that the gas pipe 105 and the indoor unit 20 are connected. The three-way linear expansion valve 37e is switched so that the indoor unit 20 and the low-pressure pipe 102 are connected.
  • the low-temperature, low-pressure refrigerant is compressed by the compressor 11 and discharged as a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 11 flows out of the outdoor unit 10 via the refrigerant flow switching device 12 and the check valve 15b and flows into the relay unit 30 .
  • the high-temperature, high-pressure gas refrigerant that has flowed into the relay unit 30 flows out of the relay unit 30 through the gas-liquid separator 31 and the three-way linear expansion valves 37a-37d, and flows into the indoor units 20a-20d.
  • the high-temperature, high-pressure gas refrigerant that has flowed into the indoor unit 20a flows into the indoor heat exchanger 22, heats the indoor air by condensing while exchanging heat with the indoor air, and flows out of the indoor heat exchanger 22 as a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant that has flowed out of the indoor heat exchanger 22 is decompressed and expanded by the indoor expansion valve 21 to become an intermediate-pressure liquid refrigerant.
  • the high-temperature and high-pressure gas refrigerants that have flowed into the indoor units 20b-20d similarly become intermediate-pressure liquid refrigerants, flow out of the indoor units 20b-20d, and flow into the relay unit 30.
  • the intermediate-pressure liquid refrigerant that has flowed into the relay unit 30 flows through the confluence pipe 108 via the check valves 36a1, 36b1, 36c1, and 36d1, and flows into the primary side passage of the second refrigerant heat exchanger 34.
  • the low-pressure liquid refrigerant that has flowed into the primary channel of the second refrigerant heat exchanger 34 is subcooled by the refrigerant flowing through the secondary channel of the second refrigerant heat exchanger 34, and flows out of the primary channel of the second refrigerant heat exchanger 34.
  • the intermediate-pressure liquid refrigerant that has flowed out of the primary-side channel of the second refrigerant heat exchanger 34 is split, and part of the liquid refrigerant flows out of the relay unit 30 via the check valve 36e2. Then, the liquid refrigerant that has flowed out of the relay unit 30 flows into the indoor unit 20e in the cooling operation.
  • the rest of the intermediate-pressure liquid refrigerant that has flowed out of the primary-side passage of the second refrigerant heat exchanger 34 passes through the branch pipe 107 and flows into the secondary-side passage of the second refrigerant heat exchanger 34 .
  • the low-pressure liquid refrigerant that has flowed into the indoor unit 20 e is decompressed and expanded by the indoor expansion valve 21 to become a low-pressure gas-liquid two-phase refrigerant or liquid refrigerant, and flows into the indoor heat exchanger 22 .
  • the low-pressure gas-liquid two-phase refrigerant or liquid refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the indoor air, absorbs heat, and evaporates to cool the indoor air, becoming a low-pressure gas refrigerant and flows out of the indoor heat exchanger 22.
  • the low-pressure gas refrigerant that has flowed out of the indoor heat exchanger 22 flows out of the indoor unit 20 e and flows into the relay unit 30 .
  • the gas refrigerant that has flowed into the relay unit 30 reaches the low-pressure pipe 102 via the three-way linear expansion valve 37e.
  • the low-pressure gas refrigerant flowing through the low-pressure pipe 102 flows out from the primary-side channel of the second refrigerant heat exchanger 34, passes through the second relay expansion valve 35, the second refrigerant heat exchanger 34, and the first refrigerant heat exchanger 32 and joins the refrigerant flowing through the branch pipe 107.
  • This low-pressure gas refrigerant flows out from the relay unit 30 and flows into the outdoor unit 10 .
  • the low-pressure gas refrigerant that has flowed into the outdoor unit 10 flows into the outdoor heat exchanger 13 via the check valve 15 c and the outdoor expansion valve 14 .
  • the low-pressure gas refrigerant that has flowed into the outdoor heat exchanger 13 exchanges heat with outdoor air, absorbs heat, evaporates, is further gasified, and flows out of the outdoor heat exchanger 13 .
  • the low-temperature, low-pressure gas refrigerant that has flowed out of the outdoor heat exchanger 13 passes through the refrigerant flow switching device 12 and the accumulator 16 and is sucked into the compressor 11 . Thereafter, the above-described circulation is repeated.
  • Evaporation temperature adjustment processing according to the first embodiment will be described.
  • the driving frequency of the compressor, the opening degree of the expansion valve, etc. are controlled so that the evaporation temperature of the refrigerating and air-conditioning system is 0° C. in order to prevent the piping of the indoor unit from freezing.
  • the longer the pipe between the indoor unit and the outdoor unit the greater the pressure loss, and the higher the evaporation temperature of the indoor unit.
  • the evaporation temperature of the indoor unit performing the cooling operation with the shortest pipe length between the indoor unit and the outdoor unit is the lowest compared to the other indoor units, and may fall below 0°C. If the evaporation temperature falls below 0°C, the pipes connected to the indoor unit may freeze and break.
  • Embodiment 1 when there are a plurality of indoor units 20 that perform cooling operation, evaporation temperature adjustment processing is performed to individually adjust the evaporation temperature of each indoor unit 20 by controlling the opening of the three-way linear expansion valve 37 provided in the relay unit 30.
  • FIG. 9 is a flowchart showing an example of the flow of evaporation temperature adjustment processing according to the first embodiment.
  • the control device 40 determines whether the current operation is the heating-dominant operation, the cooling-dominant operation, or the cooling-only operation. If the current operation is heating-dominant operation, cooling-dominant operation, or cooling-only operation (step S1: YES), the valve control unit 44 of the control device 40 sets the valve opening degrees of all the three-way linear expansion valves 37a to 37e to the initial opening degrees in step S2.
  • the initial degree of opening of the three-way linear expansion valves 37a-37e is a preset degree of opening, and is set according to the capacity of each of the three-way linear expansion valves 37a-37e.
  • step S1 NO
  • the series of processing ends.
  • step S3 the indoor pressure is detected by the indoor pressure sensor 23 provided in each of the indoor units 20a to 20e.
  • the information acquisition unit 41 acquires the indoor pressure detected by the indoor pressure sensor 23 .
  • the acquired pressure is the pressure that is considered equivalent to the evaporating pressure of the corresponding indoor heat exchanger 22 .
  • step S4 the calculation unit 42 converts the pressure, which is the evaporating pressure acquired in step S3, into the evaporating temperature of the indoor heat exchanger 22 in the indoor unit 20 that is performing cooling operation, and derives the evaporating temperature.
  • step S5 the comparison unit 43 determines whether or not the evaporation temperature of the indoor heat exchanger 22 in the indoor unit 20 that is performing the cooling operation is equal to or higher than the preset evaporation temperature. If the evaporating temperature is less than the set evaporating temperature (step S5: NO), the valve control unit 44 reduces the opening of the corresponding three-way linear expansion valve 37 by the set opening so that the evaporating temperature approaches the set evaporating temperature in step S6.
  • the valve control unit 44 reduces the opening of the three-way linear expansion valve 37a corresponding to the indoor unit 20a by the set opening.
  • the set opening degree in this case is determined in advance according to the capacity of the corresponding indoor unit 20 and the like.
  • the process proceeds to step S7.
  • step S7 the comparison unit 43 determines whether the evaporation temperature of the indoor heat exchanger 22 in the indoor unit 20 that is performing cooling operation is the set evaporation temperature. If the evaporation temperature is the set evaporation temperature (step S7: YES), the process returns to step S3.
  • step S7 if the evaporating temperature is not the set evaporating temperature (step S7: NO), the valve control unit 44 increases the opening of the corresponding three-way linear expansion valve 37 by the set opening so that the evaporating temperature approaches the set evaporating temperature in step S8. Then, the process returns to step S3.
  • the evaporation temperature of the indoor heat exchanger 22 in each indoor unit 20 can be individually adjusted. Therefore, the cooling operation can be performed according to the air-conditioning load of the room in which each indoor unit 20 is installed, and the above-described phenomenon that the room cannot be sufficiently cooled can be avoided.
  • the evaporation temperature of the indoor heat exchanger 22 is derived based on the indoor pressure detected by the indoor pressure sensor 23, but this is not limited to this example.
  • a thermocouple may be inserted into the piping of the indoor heat exchanger 22 to directly detect the refrigerant temperature, which is the evaporation temperature.
  • a thermocouple may be attached to the outer wall surface of the pipe to detect the refrigerant temperature.
  • liquid backflow suppression processing is performed to suppress liquid refrigerant from being sucked into the compressor 11 .
  • the first liquid backflow suppression process is performed when the operation mode of the refrigerating and air-conditioning apparatus 100 is the heating main operation or the heating only operation
  • the second liquid backflow suppression process is performed when the operation mode is the cooling main operation or the cooling only operation.
  • FIG. 10 is a flowchart showing an example of the flow of liquid backflow suppression processing according to the first embodiment.
  • control device 40 determines whether or not the operation mode of refrigerating and air-conditioning apparatus 100 is heating main operation or heating only operation.
  • step S100: YES When the operation mode is heating-main operation or heating-only operation (step S100: YES), the control device 40 performs the first liquid backflow suppression process in step S10. On the other hand, if the operation mode is not the heating-main operation or the heating-only operation, that is, if the operation mode is the cooling-main operation or the cooling-only operation (step S100: NO), the control device 40 performs the second liquid backflow suppression process in step S30.
  • FIG. 11 is a flow chart showing an example of the flow of the first liquid bagging suppression process of FIG.
  • step S ⁇ b>11 the suction pressure P ⁇ b>17 of the refrigerant sucked into the compressor 11 is detected by the outdoor pressure sensor 17 provided in the outdoor unit 10 .
  • the information acquisition unit 41 acquires the suction pressure P17 detected by the outdoor pressure sensor 17 .
  • the acquired suction pressure P ⁇ b>17 is the pressure that is considered equivalent to the evaporation pressure of the outdoor heat exchanger 13 .
  • step S12 the intake temperature T18 of the refrigerant sucked into the compressor 11 is detected by the outdoor temperature sensor 18 provided in the outdoor unit 10.
  • the information acquisition unit 41 acquires the intake temperature T18 detected by the outdoor temperature sensor 18 .
  • step S13 the calculation unit 42 converts the suction pressure P17, which is the evaporating pressure acquired in step S11, into the evaporating temperature Te of the outdoor heat exchanger 13, and derives the evaporating temperature Te.
  • step S15 the comparison unit 43 determines whether the degree of superheat SH1 is equal to or less than the set degree of superheat. If the degree of superheat SH1 is less than or equal to the set degree of superheat (step S15: YES), the process proceeds to step S16. On the other hand, if the degree of superheat SH1 is less than the set degree of superheat (step S15: NO), the process returns to step S11.
  • step S16 the valve control unit 44 reduces the opening of the three-way linear expansion valve 37 corresponding to the indoor unit 20 that is performing the cooling operation by the set opening so that the refrigerant sucked into the compressor 11 does not back up.
  • the set opening degree in this case is determined in advance according to the amount of refrigerant in the refrigerating and air-conditioning apparatus 100, the outside air temperature, the refrigerant pressure, the refrigerant temperature, and the like.
  • step S17 the suction pressure P17 is detected by the outdoor pressure sensor 17, and the information acquisition unit 41 acquires the suction pressure P17 detected by the outdoor pressure sensor 17.
  • step S ⁇ b>18 the intake temperature T ⁇ b>18 is detected by the outdoor temperature sensor 18 , and the valve control unit 44 acquires the intake temperature T ⁇ b>18 detected by the outdoor temperature sensor 18 .
  • step S19 the calculation unit 42 converts the suction pressure P17 acquired in step S17 into the evaporation temperature Te of the outdoor heat exchanger 13 to derive the evaporation temperature Te.
  • step S20 the calculation unit 42 calculates the degree of superheat SH1 based on the intake temperature T18 acquired in step S18 and the evaporation temperature Te derived in step S19.
  • step S21 the comparison unit 43 determines whether the degree of superheat SH1 is equal to or less than the set degree of superheat. If the degree of superheat SH1 is less than or equal to the set degree of superheat (step S21: YES), the process proceeds to step S22. On the other hand, if the degree of superheat SH1 is less than the set degree of superheat (step S21: NO), the process returns to step S11.
  • step S22 the valve control unit 44 reduces the opening of the outdoor expansion valve 14 provided in the outdoor unit 10 by the set opening so that the refrigerant sucked into the compressor 11 does not back up. Then, the process returns to step S11.
  • the first liquid backflow suppression process is performed when the heating main operation or the heating only operation is being performed.
  • the liquid refrigerant can be reliably gasified before the refrigerant is sucked into the compressor 11, so that the compressor 11 can be prevented from malfunctioning.
  • the first liquid backflow suppression process is performed in parallel with the above-described evaporation temperature adjustment process.
  • both processes include a step of controlling the degree of opening of the three-way linear expansion valve 37, but when the degree of superheat SH1 of the refrigerant sucked into the compressor 11 falls below the set degree of superheat, the protection of the compressor 11 is prioritized. That is, priority is given to the opening degree control of the three-way linear expansion valve 37 performed in step S16 of the first liquid back suppression process.
  • FIG. 12 is a flow chart showing an example of the flow of the second liquid bagging suppression process of FIG.
  • step S ⁇ b>31 the suction pressure P ⁇ b>17 of the refrigerant sucked into the compressor 11 is detected by the outdoor pressure sensor 17 provided in the outdoor unit 10 .
  • the information acquisition unit 41 acquires the suction pressure P17 detected by the outdoor pressure sensor 17 .
  • step S32 the intake temperature T18 of the refrigerant sucked into the compressor 11 is detected by the outdoor temperature sensor 18 provided in the outdoor unit 10.
  • the information acquisition unit 41 acquires the intake temperature T18 detected by the outdoor temperature sensor 18 .
  • step S33 the calculation unit 42 converts the suction pressure P17 acquired in step S11 into the evaporation temperature Te of the outdoor heat exchanger 13 to derive the evaporation temperature Te.
  • step S35 the comparison unit 43 determines whether the degree of superheat SH2 is equal to or less than the set degree of superheat. If the degree of superheat SH2 is equal to or less than the set degree of superheat (step S35: YES), the process proceeds to step S36. On the other hand, when the degree of superheat SH2 is less than the set degree of superheat (step S35: NO), the process returns to step S31.
  • step S36 the valve control unit 44 reduces the opening of the indoor expansion valve 21 provided in the indoor unit 20 that is performing the heating operation by the set opening so that the refrigerant sucked into the compressor 11 does not back up.
  • step S37 the suction pressure P17 is detected by the outdoor pressure sensor 17, and the information acquisition unit 41 acquires the suction pressure P17 detected by the outdoor pressure sensor 17.
  • step S ⁇ b>38 the intake temperature T ⁇ b>18 is detected by the outdoor temperature sensor 18 , and the information acquisition unit 41 acquires the intake temperature T ⁇ b>18 detected by the outdoor temperature sensor 18 .
  • step S39 the calculation unit 42 converts the suction pressure P17 acquired in step S37 into the evaporation temperature Te of the outdoor heat exchanger 13 to derive the evaporation temperature Te.
  • step S40 the calculation unit 42 calculates the degree of superheat SH2 based on the suction temperature T18 acquired in step S38 and the evaporation temperature Te derived in step S39.
  • step S41 the comparison unit 43 determines whether the degree of superheat SH2 is equal to or less than the set degree of superheat.
  • step S41: YES the degree of superheat SH2 is equal to or less than the set degree of superheat
  • step S41: NO the degree of superheat SH2 is less than the set degree of superheat
  • step S42 the valve control unit 44 reduces the opening of the three-way linear expansion valve 37 corresponding to the indoor unit 20 that is performing the cooling operation by the set opening so that the refrigerant sucked into the compressor 11 does not back up. Then, the process returns to step S31.
  • the second liquid backflow suppression process is performed when the cooling-main operation or the cooling-only operation is being performed.
  • the liquid refrigerant can be reliably gasified before the refrigerant is sucked into the compressor 11, so that the compressor 11 can be prevented from malfunctioning.
  • both processes include a step of controlling the opening degree of the three-way linear expansion valve 37, but when the degree of superheat SH2 of the refrigerant sucked into the compressor 11 falls below the set degree of superheat, the protection of the compressor 11 is prioritized. That is, priority is given to the opening degree control of the three-way linear expansion valve 37 performed in step S42 of the second liquid back suppression process.
  • the opening degree of the corresponding three-way linear expansion valve 37 is controlled based on the indoor pressure of the indoor unit 20 that is performing cooling operation.
  • the evaporating temperature is derived from the indoor pressure of the indoor unit 20 that is performing cooling operation, and the opening of the three-way linear expansion valve 37 is controlled according to the comparison result between the evaporating temperature and the set evaporating temperature.
  • the evaporation temperature is adjusted for each indoor unit 20 that is performing cooling operation, so each indoor unit can be individually controlled.
  • the evaporation temperature is derived from the suction pressure, and the degree of superheat is calculated based on the suction temperature and the evaporation temperature. Then, when the degree of superheat is equal to or less than the constant degree of superheat, the degree of opening of at least one of the three-way linear expansion valve 37, the outdoor expansion valve 14, and the indoor expansion valve 21 is controlled. As a result, the refrigerant sucked into the compressor 11 can be sufficiently superheated, so liquid backflow to the compressor 11 can be suppressed.
  • Embodiment 2 A second embodiment will be described. Embodiment 2 is different from Embodiment 1 in that an indoor unit that draws outside air and blows it into the room is used. It should be noted that, in the second embodiment, the same reference numerals are assigned to the parts that are common to the first embodiment, and detailed description thereof will be omitted.
  • FIG. 13 is a circuit diagram showing an example of the configuration of the refrigerating and air-conditioning apparatus according to the second embodiment.
  • a refrigerating and air-conditioning apparatus 100 ⁇ /b>A according to Embodiment 2 includes an outdoor unit 10 , a plurality of indoor units 120 , a relay unit 30 and a control device 40 .
  • the refrigerating and air-conditioning apparatus 100A is composed of one outdoor unit 10, five indoor units 120a to 120e, and one relay unit 30.
  • FIG. 13 is a circuit diagram showing an example of the configuration of the refrigerating and air-conditioning apparatus according to the second embodiment.
  • a refrigerating and air-conditioning apparatus 100 ⁇ /b>A according to Embodiment 2 includes an outdoor unit 10 , a plurality of indoor units 120 , a relay unit 30 and a control device 40 .
  • the refrigerating and air-conditioning apparatus 100A is composed of one outdoor unit 10, five indoor units 120a to 120e, and one relay unit 30.
  • a refrigerant circuit is formed by connecting the outdoor unit 10, the relay unit 30, and the indoor units 120a to 120e with the high-pressure pipe 101 and the low-pressure pipe .
  • the number of indoor units 120 is not limited to this example, and may be two or more and four or less, or may be six or more.
  • FIG. 13 omits the configuration connected to the indoor units 120c and 120d among the circuit configurations of the indoor units 120c and 120d and the relay unit 30. Also, the circuit configuration of the indoor units 120b and 120e is the same as that of the indoor unit 120a, so illustration thereof is omitted.
  • the configurations of the outdoor unit 10, the relay unit 30 and the control device 40 are the same as those of Embodiment 1, and thus descriptions thereof are omitted here.
  • the indoor units 120a to 120e take in outside air to perform air conditioning, and then blow out the conditioned air into the room. In this manner, the indoor units 120a to 120e perform air conditioning on the outside air that is drawn in and blow out the conditioned air indoors, so that the rooms 1a to 1e can be cooled or heated while being ventilated.
  • the indoor units 120a to 120e are provided with an outside air inlet 151 for sucking outside air and an outlet 152 for blowing out air.
  • Each of the indoor units 120a-120e includes an indoor expansion valve 21 and an indoor heat exchanger 122.
  • the indoor units 120a to 120e are provided with an indoor pressure sensor 23 and a blown air temperature sensor 24, respectively.
  • the indoor units 120a to 120e are simply referred to as "indoor unit 120" when there is no particular need to distinguish them.
  • the indoor heat exchanger 122 exchanges heat between the refrigerant and outside air supplied from the outside air suction port 151 by a blower such as a fan (not shown). As a result, heating air or cooling air to be supplied to the rooms 1a to 1e is generated.
  • the blowout air temperature sensor 24 is provided at the blowout port 152 of the indoor unit 120 . Blown air temperature sensor 24 detects a blown air temperature, which is the temperature of the air blown out from outlet 152 .
  • all the indoor units provided in the refrigerating and air-conditioning apparatus 100A are described as indoor units 120 that draw outside air, but this is not limited to this example.
  • the refrigerating and air-conditioning apparatus 100A may use at least one indoor unit as the indoor unit 120 that draws outside air, and the remaining indoor units as the indoor units 20 described in the first embodiment.
  • control device 40 controls the opening degrees of the indoor expansion valve 21 of the indoor unit 120 and the three-way linear expansion valve 37 of the relay unit 30 so that the blown air temperature detected by the blown air temperature sensor 24 of the indoor unit 120 becomes the set temperature.
  • the refrigerating and air-conditioning apparatus 100A according to Embodiment 2 uses the indoor unit 120 that draws in the outside air and blows it out. As a result, the same effect as in the first embodiment can be obtained while ventilating the room in which the indoor unit 120 is installed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un dispositif de réfrigération et de climatisation qui comprend : une unité externe ayant un compresseur et un échangeur de chaleur externe ; une pluralité d'unités internes ayant chacune un détendeur interne et un échangeur de chaleur interne ; une unité de relais connectée entre l'unité externe et les unités internes et ayant une pluralité de soupapes à trois voies qui sont disposées en correspondance avec le nombre des unités internes de façon à commuter l'écoulement de fluide frigorigène et à réguler le débit du fluide frigorigène passant, l'unité de relais distribuant un fluide frigorigène à basse température vers une unité interne qui effectue un fonctionnement de refroidissement et un fluide frigorigène à haute température vers une unité interne qui effectue une opération de chauffage ; et un dispositif de commande qui commande le degré de commutation et d'ouverture des soupapes à trois voies. Les unités internes comportent chacune un capteur de pression côté interne qui détecte la pression côté interne, qui est la pression du fluide frigorigène traversant l'échangeur de chaleur interne. Le dispositif de commande commande le degré d'ouverture de la soupape à trois voies correspondante afin d'ajuster le débit du fluide frigorigène passant sur la base de la pression côté interne de l'unité interne qui effectue l'opération de refroidissement.
PCT/JP2022/001823 2022-01-19 2022-01-19 Dispositif de réfrigération et de climatisation Ceased WO2023139700A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP22921859.9A EP4467897A4 (fr) 2022-01-19 2022-01-19 Dispositif de réfrigération et de climatisation
US18/709,579 US20250003646A1 (en) 2022-01-19 2022-01-19 Refrigerating and air-conditioning apparatus
JP2023574952A JPWO2023139700A1 (fr) 2022-01-19 2022-01-19
PCT/JP2022/001823 WO2023139700A1 (fr) 2022-01-19 2022-01-19 Dispositif de réfrigération et de climatisation
JP2025083210A JP2025114842A (ja) 2022-01-19 2025-05-19 冷凍空調装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/001823 WO2023139700A1 (fr) 2022-01-19 2022-01-19 Dispositif de réfrigération et de climatisation

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5989959A (ja) * 1982-11-11 1984-05-24 松下精工株式会社 分離形空気調和機
JPH0771839A (ja) * 1993-06-30 1995-03-17 Mitsubishi Electric Corp ヒートポンプシステム
JPH07305879A (ja) * 1994-05-10 1995-11-21 Daikin Ind Ltd マルチ形空気調和機の誤配線検出方法
JPH0875226A (ja) * 1994-09-01 1996-03-19 Daikin Ind Ltd マルチ形空気調和機
JPH08145483A (ja) * 1994-11-18 1996-06-07 Matsushita Electric Ind Co Ltd 空気調和機
JPH10325589A (ja) * 1997-05-22 1998-12-08 Daikin Ind Ltd 熱回収型空気調和装置
JP2003343936A (ja) * 2002-05-28 2003-12-03 Mitsubishi Electric Corp 冷凍サイクル装置
WO2018155056A1 (fr) 2017-02-24 2018-08-30 ダイキン工業株式会社 Climatiseur

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH068697B2 (ja) * 1987-11-02 1994-02-02 株式会社日立製作所 外気導入形空気調和機及びその運転方法
JP2522360B2 (ja) * 1988-10-12 1996-08-07 三菱電機株式会社 空気調和装置
JPH05187730A (ja) * 1992-01-14 1993-07-27 Mitsubishi Heavy Ind Ltd 空気調和機
JPH10253187A (ja) * 1997-03-12 1998-09-25 Hitachi Ltd 空気調和機
JP2007292429A (ja) * 2006-04-27 2007-11-08 Daikin Ind Ltd 空気調和装置
WO2014106901A1 (fr) * 2013-01-07 2014-07-10 三菱電機株式会社 Dispositif de climatisation

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5989959A (ja) * 1982-11-11 1984-05-24 松下精工株式会社 分離形空気調和機
JPH0771839A (ja) * 1993-06-30 1995-03-17 Mitsubishi Electric Corp ヒートポンプシステム
JPH07305879A (ja) * 1994-05-10 1995-11-21 Daikin Ind Ltd マルチ形空気調和機の誤配線検出方法
JPH0875226A (ja) * 1994-09-01 1996-03-19 Daikin Ind Ltd マルチ形空気調和機
JPH08145483A (ja) * 1994-11-18 1996-06-07 Matsushita Electric Ind Co Ltd 空気調和機
JPH10325589A (ja) * 1997-05-22 1998-12-08 Daikin Ind Ltd 熱回収型空気調和装置
JP2003343936A (ja) * 2002-05-28 2003-12-03 Mitsubishi Electric Corp 冷凍サイクル装置
WO2018155056A1 (fr) 2017-02-24 2018-08-30 ダイキン工業株式会社 Climatiseur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4467897A4

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JP2025114842A (ja) 2025-08-05
EP4467897A4 (fr) 2025-02-26
EP4467897A1 (fr) 2024-11-27
JPWO2023139700A1 (fr) 2023-07-27
US20250003646A1 (en) 2025-01-02

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